Blade elevation mechanisms and anti-backdrive mechanisms for table saws

ABSTRACT

Elevation mechanisms for table saws and anti-backdrive mechanisms for use in elevation mechanisms for table saws are disclosed. The anti-backdrive mechanisms typically include three sub-assemblies: an input assembly, an output assembly, and a fixed assembly. The anti-backdrive mechanisms prevent a torque related to the output assembly from changing the blade elevation. For example, the weight of the blade and the structure supporting the blade is prevented from backdriving the elevation mechanism and allowing the blade to drop.

CROSS-REFERENCE TO RELATED APPLICATION

This application claims the benefit of and priority from U.S.Provisional Patent Application Ser. No. 61/741,461, filed Jul. 20, 2012,which is incorporated herein by reference.

TECHNICAL FIELD

The present disclosure relates to table saw mechanisms designed toimprove convenience and performance. More specifically, thisspecification relates to elevation mechanisms used to raise and lowerblades on table saws.

BACKGROUND

A table saw is a power tool used to cut a workpiece to a desired size orshape. A table saw includes a work surface or table and a circular bladeextending up through the table. A person uses a table saw by placing apiece of wood or other workpiece on the table and feeding it past thespinning blade to make a cut.

Table saws are typically constructed so that a user can adjust theelevation of the blade above the table in order to cut workpieces ofvarying thicknesses. When making a cut the blade is often raised justhigh enough to cut through the workpiece so the blade is exposed aslittle as possible in case of an accident. Often table saws include ahandwheel that turns gears to raise and lower the blade. A user simplyturns the handwheel clockwise, for example, to raise the blade, andcounterclockwise to lower the blade. However, in small table saws suchas jobsite and benchtop saws, handwheels typically must be turned manytimes to move the blade from a fully retracted position to a fullyelevated position. For example, a handwheel might have to be turnedapproximately twenty, thirty or even forty revolutions to move the bladethrough its full range of elevation. This is a time consuming andinconvenient process.

This disclosure describes several elevation mechanisms, many of whichenable a user to raise or lower the blade by turning the handle only onerevolution or only a relatively small number of revolutions.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 shows a table saw.

FIG. 2 shows an anti-backdrive mechanism attached to an input shaft witha handwheel at one end and an output shaft with a pulley at the otherend.

FIG. 3 shows an input assembly incorporating the release plate of theanti-backdrive mechanism of FIG. 2 attached to an input shaft.

FIG. 4 shows an output assembly incorporating the flange and ramp platesof the anti-backdrive mechanism of FIG. 2 attached to an output shaft.

FIG. 5 shows a fixed assembly incorporating the vertical plate of theanti-backdrive mechanism of FIG. 2.

FIG. 6 shows the input assembly of FIG. 3, the output assembly of FIG. 4and the fixed assembly of FIG. 5 assembled together.

FIG. 7 shows a perspective view of the release plate in theanti-backdrive mechanism of FIG. 6.

FIG. 8 shows another perspective view of the release plate of FIG. 7.

FIG. 9 shows a front view of the release plate of FIG. 7.

FIG. 10 shows a rear view of the release plate of FIG. 7.

FIG. 11 shows a side view of the release plate of FIG. 7.

FIG. 12 shows an input assembly incorporating an alternative releaseplate for the anti-backdrive mechanism of FIG. 6.

FIG. 13 shows an exploded view of the alternative input assembly shownin FIG. 12.

FIG. 14 shows a perspective view of the alternative release plate ofFIG. 12.

FIG. 15 shows a front view of the alternative release plate of FIG. 12.

FIG. 16 shows a side view of the alternative release plate of the inputassembly of FIG. 12.

FIG. 17 shows a perspective view of a release plate coupler of the inputassembly of FIG. 12.

FIG. 18 shows another perspective view of a release plate coupler ofFIG. 17.

FIG. 19 shows a rear view of a release plate coupler of FIG. 17.

FIG. 20 shows a front view of a release plate coupler of FIG. 17.

FIG. 21 shows the input assembly of FIG. 3 with a torsion springinstalled in the release plate.

FIG. 22 shows a perspective view of the torsion spring of FIG. 21.

FIG. 23 shows a front view of the torsion spring of FIG. 22.

FIG. 24 shows a side view of the torsion spring of FIG. 22.

FIG. 25 shows a perspective view of the flange plate of theanti-backdrive mechanism of FIG. 6.

FIG. 26 shows a front view of the flange plate of FIG. 25.

FIG. 27 shows another perspective view of the flange plate of FIG. 25.

FIG. 28 shows a side view of the flange plate of FIG. 25.

FIG. 29 shows the torsion spring of FIG. 22 and locking springs withlocking cylinders situated on the flange plate of the anti-backdrivemechanism shown in FIG. 6.

FIG. 30 shows a perspective view of the locking spring shown in FIG. 29.

FIG. 31 shows a front view of the locking spring of FIG. 30.

FIG. 32 shows a side view of the locking spring of FIG. 30.

FIG. 33 shows another perspective view of the anti-backdrive mechanismof FIG. 6.

FIG. 34 shows a rear view of the ramp plate of the anti-backdrivemechanism of FIG. 6.

FIG. 35 shows a front view of the ramp plate of FIG. 34.

FIG. 36 shows a side view of the ramp plate of FIG. 34.

FIG. 37 shows a perspective view of the ramp plate of FIG. 34.

FIG. 38 shows a cross-sectional view of the ramp plate of FIG. 34, takenalong line A-A in FIG. 34, showing ramped surfaces that the lockingcylinders shown in FIG. 29 contact.

FIG. 39 shows the anti-backdrive mechanism of FIG. 6 with foam filters.

FIG. 40 shows the anti-backdrive mechanism of FIG. 6 with a dust cover.

FIG. 41 shows a perspective view of the dust cover of FIG. 40.

FIG. 42 shows another perspective view of the dust cover of FIG. 40.

FIG. 43 shows the anti-backdrive mechanism of FIG. 6 driving anelevation mechanism that raises and lowers a blade and is in a fullyraised position.

FIG. 44 shows the anti-backdrive mechanism of FIG. 6 driving anelevation mechanism that raises and lowers a blade and is in a fullylowered position.

FIG. S1 shows an input assembly of an anti-backdrive mechanism shown inFIG. S4.

FIG. S2 shows an output assembly of an anti-backdrive mechanism shown inFIG. S4.

FIG. S3 shows a fixed assembly of an anti-backdrive mechanism shown inFIG. S4.

FIG. S4 shows a spring lock anti-backdrive mechanism assemblyincorporating the input assembly of FIG. S1, the output assembly of FIG.S2 and the fixed assembly of FIG. S3.

FIG. S5 shows a perspective view of the input shaft of the inputassembly in FIG. S1.

FIG. S6 shows a perspective view of the input arm of the input assemblyin FIG. S1.

FIG. S7 shows another perspective view of the input arm of FIG. 56.

FIG. S8 shows a perspective view of the torsion spring of the inputassembly in FIG. S1.

FIG. S9 shows a perspective view of the output shaft of the outputassembly in FIG. S2.

FIG. S10 shows a perspective view of the output arm of the outputassembly in FIG. S2.

FIG. S11 shows a perspective view of the mounting block of the fixedassembly in FIG. S3.

FIG. S12 shows a perspective view of the spilt cylinder of the fixedassembly in FIG. S3.

FIG. S13 shows a side view of the split cylinder of FIG. S12.

FIG. S14 shows another perspective view of the split cylinder of FIG.S12.

FIG. 515 shows a perspective view of the hose clamp of the fixedassembly in FIG. S3.

FIG. S16 shows a side view of the anti-backdrive mechanism assembly ofFIG. S4.

FIG. S17 shows a side view of the input and output assemblies of FIGS.S1 and S2 put together.

FIG. S18 shows a perspective view of the torsion spring of FIG. S8placed over the end of the output assembly of FIG. 52.

FIG. S19 shows a cross-sectional view of section A-A shown in FIG. S17which illustrates the input and output arms of FIGS. S6 and S10positioned within the torsion spring of FIG. S8.

FIG. S20 shows the cross-sectional view of FIG. S19 but with the outputarm rotated within the torsion spring and the consequent deformation ofthe torsion spring.

FIG. S21 shows the cross-sectional view of FIG. S19 but with the inputarm rotated within the torsion spring and the consequent deformation ofthe torsion spring.

FIG. U1 shows an input assembly of an anti-backdrive mechanism shown inFIG. U4.

FIG. U2 shows an output assembly of an anti-backdrive mechanism shown inFIG. U4.

FIG. U3 shows a fixed assembly of an anti-backdrive mechanism shown inFIG. U4.

FIG. U4 shows a spring lock anti-backdrive mechanism assemblyincorporating the input assembly of FIG. U1, the output assembly of FIG.U2 and the fixed assembly of FIG. U3.

FIG. U5 shows an exploded view of the fixed assembly of FIG. U3.

FIG. U6 shows a front view of the spring in the fixed assembly of FIG.U5.

FIG. U7 shows a side view of the spring in FIG. U6.

FIG. U8 shows an exploded view of the input assembly of FIG. U1.

FIG. U9 shows a perspective view of the input engager of the inputassembly of FIG. U8.

FIG. U10 shows a side view of the input engager of the input assembly ofFIG. U8.

FIG. U11 shows a rear view of the input engager of the input assembly ofFIG. U8.

FIG. U12 shows an exploded view of the output assembly of FIG. U2.

FIG. U13 shows a perspective view of the output engager of the outputassembly of FIG. U12.

FIG. U14 shows a side view of the output engager of the output assemblyof FIG. U12.

FIG. U15 shows another perspective view of the output engager of theoutput assembly of FIG. U12.

FIG. U16 shows a side view of the anti-backdrive mechanism assembly inFIG. U4.

FIG. U17 shows a perspective view of a portion of the anti-backdrivemechanism assembly in FIG. U4 showing the spring relative to the inputand output engagers.

FIG. U18 shows a front view of the nested input and output assembliesshowing the ends of the spring sticking out the sides of the input andoutput engagers.

FIG. B1 shows an input assembly of an anti-backdrive mechanism shown inFIG. B4.

FIG. B2 shows an output assembly of an anti-backdrive mechanism shown inFIG. B4.

FIG. B3 shows a fixed assembly of an anti-backdrive mechanism shown inFIG. B4.

FIG. B4 shows an anti-backdrive mechanism assembly incorporating theinput assembly of FIG. B1, the output assembly of FIG. B2 and the fixedassembly of FIG. B3.

FIG. B5 shows an exploded view of the input assembly of FIG. B1.

FIG. B6 shows a perspective view of the input hinge of theanti-backdrive mechanism of FIG. B4.

FIG. B7 shows a top view of the input hinge of the anti-backdrivemechanism of FIG. B4.

FIG. B8 shows a side view of the input hinge of the anti-backdrivemechanism of FIG. B4.

FIG. B9 shows a front view of the input hinge of the anti-backdrivemechanism of FIG. B4.

FIG. B10 shows an exploded view of the output assembly of FIG. B2.

FIG. B11 shows a perspective view of the output hinge of theanti-backdrive mechanism of FIG. B4.

FIG. B12 shows a top view of the output hinge of the anti-backdrivemechanism of FIG. B4.

FIG. B13 shows a side view of the output hinge of the anti-backdrivemechanism of FIG. B4.

FIG. B14 shows a front view of the output hinge of the anti-backdrivemechanism of FIG. B4.

FIG. B15 shows a perspective view of a plate.

FIG. B16 shows a front view of a plate.

FIG. B17 shows an exploded view of the fixed assembly of FIG. B3.

FIG. B18 shows the input assembly of FIG. B1 assembled with the outputassembly of FIG. B2.

FIG. B19 shows a perspective view of the input hinge of the inputassembly of FIG. B1 nested with the output hinge of the output assemblyof FIG. B2.

FIG. B20 shows a front view of the nested input and output hinges withplates and a spring.

FIG. B21 shows the input assembly of FIG. B1 assembled with the outputassembly of FIG. B2 and the fixed cylinder of the fixed assembly in FIG.B3.

FIG. B22 shows a diagram that illustrates a plate extending past theoutput hinge when it does not lie along the diameter of the outputhinge.

FIG. P1 shows an input assembly of an anti-backdrive mechanism shown inFIG. P4.

FIG. P2 shows an output assembly of an anti-backdrive mechanism shown inFIG. P4.

FIG. P3 shows a fixed assembly of an anti-backdrive mechanism shown inFIG. P4.

FIG. P4 shows an anti-backdrive mechanism assembly incorporating theinput assembly of FIG. P1, the output assembly of FIG. P2 and the fixedassembly of FIG. P3.

FIG. P5 shows an exploded view of the input assembly of Figure P1.

FIG. P6 shows a perspective view of the input hinge of the inputassembly in FIG. P1.

FIG. P7 shows another perspective view of the input hinge of the inputassembly in FIG. P1.

FIG. P8 shows a side view of the input hinge of the input assembly inFIG. P1.

FIG. P9 shows a rear view of the input hinge of the input assembly inFIG. P1.

FIG. P10 shows an exploded view of the output assembly of Figure P2.

FIG. P11 shows a perspective view of the output hinge of the outputassembly in FIG. P2.

FIG. P12 shows another perspective view of the output hinge of theoutput assembly in FIG. P2.

FIG. P13 shows a side view of the output hinge of the output assembly inFIG. P2.

FIG. P14 shows a front view of the output hinge of the output assemblyin FIG. P2.

FIG. P15 shows an exploded view of the fixed assembly of Figure P3.

FIG. P16 shows the input assembly of FIG. P1 installed in the fixedassembly of FIG. P3.

FIG. P17 shows a ?side\front? view of a plate of the fixed assembly ofFIG. P3 isolated.

FIG. P18 shows a ?side? view of a plate of the fixed assembly of FIG. P3isolated.

FIG. P19 shows a rear view of the fixed assembly of FIG. P3 installed onthe output assembly of FIG. P2.

FIG. P20 shows a rear view of the input hinge, output hinge, plates andsprings of the anti-backdrive mechanism of FIG. P4.

FIG. P21 shows a rear view of the input hinge, output hinge, fixedcylinder, plates and springs of the anti-backdrive mechanism of FIG. P4in the default configuration with the output hinge transparent.

FIG. P22 shows the view of FIG. P21 with markings that show thedirection that two plates would tend to rotate when the output hingestarts to rotate.

FIG. P23 a shows the view of FIG. P21 with markings that show thedirection that two plates would tend to rotate when the input hingestarts to rotate.

FIG. P23 b shows a rear view of the input hinge, output hinge, fixedcylinder, plates and springs of the anti-backdrive mechanism of FIG. P4with two of the plates rotated to a new position by the input hinge.

FIG. P23 c shows the view of FIG. P23 b with markings that show thedirection that two plates would tend to rotate as the input hinge isfurther rotated.

FIG. P23 d shows a rear view of the input hinge, output hinge, platesand springs of the anti-backdrive mechanism of FIG. P4 in a released orunlocked state with all four plates rotated and with markings that showthe rotation of the input hinge, output hinge and plates.

FIG. C1 shows an input assembly of an anti-backdrive mechanism shown inFIG. C4.

FIG. C2 shows an output assembly of an anti-backdrive mechanism shown inFIG. C4.

FIG. C3 shows a fixed assembly of an anti-backdrive mechanism shown inFIG. C4.

FIG. C4 shows an anti-backdrive mechanism assembly incorporating theinput assembly of FIG. C1, the output assembly of FIG. C2 and the fixedassembly of FIG. C3.

FIG. C5 shows an exploded view of the input assembly of Figure C1.

FIG. C6 shows a top view of the input assembly of FIG. C1.

FIG. C7 shows a side view of the right input shaft plate of the inputassembly of FIG. C1.

FIG. C8 shows another side view of the input shaft plate of FIG. C7.

FIG. C9 shows a front view of the input shaft plate of FIG. C7.

FIG. C10 shows an exploded view of the output assembly of FIG. C2.

FIG. C11 shows an top view of the output shaft in the output assembly ofFIG. C2.

FIG. C12 shows a side view of the output shaft in the output assembly ofFIG. C2.

FIG. C13 shows a front view of the output shaft in the output assemblyof FIG. C2.

FIG. C14 shows a side view of the output shaft plate in the outputassembly of FIG. C2.

FIG. C15 shows a front view of the collar in the output assembly of FIG.C2.

FIG. C16 shows an exploded view of the fixed assembly of Figure C3.

FIG. C17 shows a front view of the brake plate in the fixed assembly ofFIG. C3.

FIG. C18 shows a top view of a rotating plate in the fixed assembly ofFIG. C3.

FIG. C19 shows a side view of a rotating plate in the fixed assembly ofFIG. C3.

FIG. C20 shows a top view of the anti-backdrive mechanism of FIG. C4 ina locked configuration with the output shaft slightly rotated and therotating plates spread apart.

FIG. C21 shows a front view of the anti-backdrive mechanism in thelocked configuration shown in FIG. C20.

FIG. C22 shows a top view of the anti-backdrive mechanism of FIG. C4 inan unlocked, or released, configuration with the input shaft slightlyrotated and the rotating plates perpendicular to the brake plate.

FIG. C23 shows a front view of the anti-backdrive mechanism in theunlocked configuration shown in FIG. C22.

FIG. A1 shows an input assembly of an anti-backdrive mechanism shown inFIG. A4.

FIG. A2 shows an output assembly of an anti-backdrive mechanism shown inFIG. A4.

FIG. A3 shows a fixed assembly of an anti-backdrive mechanism shown inFIG. A4.

FIG. A4 shows an anti-backdrive mechanism assembly incorporating theinput assembly of FIG. A1, the output assembly of FIG. A2 and the fixedassembly of FIG. A3.

FIG. A5 shows an exploded view of the input assembly of Figure A1.

FIG. A6 shows a side view of the input cylinder of the input assemblyshown in FIG. A1.

FIG. A7 shows a top view of the input cylinder of the input assemblyshown in FIG. A1.

FIG. A8 shows a font view of the input cylinder of the input assemblyshown in FIG. A1.

FIG. A9 shows an exploded view of the output assembly of Figure A2.

FIG. A10 shows a side view of the output cylinder of the input assemblyshown in FIG. A2.

FIG. A11 shows a font view of the output cylinder of the input assemblyshown in FIG. A2.

FIG. A12 shows a top view of the output cylinder of the input assemblyshown in FIG. A2.

FIG. A13 shows a bottom view of the output cylinder of the inputassembly shown in FIG. A2.

FIG. A14 shows an exploded view of the fixed assembly of Figure A3.

FIG. A15 shows a perspective view of the movable plate assembly of thefixed assembly of FIG. A3.

FIG. A16 shows a side view of the movable plate assembly of FIG. A15.

FIG. A17 shows a top view of the movable plate assembly of Figure A15.

FIG. A18 shows a perspective view of one of the rectangular slab of themovable plate assembly of FIG. A15.

FIG. A19 shows a side view of the rectangular slab of FIG. A18.

FIG. A20 shows a top view of the rectangular slab of FIG. A18.

FIG. A21 shows a perspective view of the H block of the movable plateassembly of FIG. A15.

FIG. A22 shows a side view of the H block of FIG. A21.

FIG. A23 shows a side view of the anti-backdrive mechanism assembly ofFIG. A4.

FIG. A24 shows a side view of the anti-backdrive mechanism assembly ofFIG. A4 with the output shaft slightly rotated.

FIG. A25 shows a side view of the anti-backdrive mechanism assembly ofFIG. A4 with the input shaft slightly rotated.

FIG. T1 shows the input assembly of an anti-backdrive mechanism shown inFIG. T4.

FIG. T2 shows the output assembly of an anti-backdrive mechanism shownin FIG. T4.

FIG. T3 shows the fixed assembly of an anti-backdrive mechanism shown inFIG. T4.

FIG. T4 shows an anti-backdrive mechanism assembly incorporating theinput assembly of FIG. T1, the output assembly of FIG. T2 and the fixedassembly of FIG. T3.

FIG. T5 shows a cross-sectional view of one end of the input shaft inthe input assembly of FIG. T1.

FIG. T6 shows a perspective view of the spring in the input assembly ofFIG. T1.

FIG. T7 shows a front view of the spring in the input assembly of FIG.T1.

FIG. T8 shows a side view of the spring in the input assembly of FIG.T1.

FIG. T9 shows a rear view of the input assembly of FIG. T1 where thespring can be seen wrapped around the end of the input shaft.

FIG. T10 shows an exploded view of the fixed assembly of Figure T3.

FIG. T11 shows a side view of the input assembly of FIG. T1 along withthe output shaft of the output assembly of FIG. T2.

FIG. T12 shows a side view of the input assembly of FIG. T1 along withthe output shaft of the output assembly of FIG. T2 and the fixedassembly of FIG. T3.

FIG. TB1 shows the input assembly of an anti-backdrive mechanism shownin FIG. T4.

FIG. TB2 shows the output assembly of an anti-backdrive mechanism shownin FIG. T4.

FIG. TB3 shows the fixed assembly of an anti-backdrive mechanism shownin FIG. T4.

FIG. TB4 shows an anti-backdrive mechanism assembly incorporating theinput assembly of FIG. TB1, the output assembly of FIG. TB2 and thefixed assembly of FIG. TB3.

FIG. TB5 shows an exploded view of the input assembly of Figure TB1.

FIG. TB6 shows a rear view of the input shaft of the input assembly ofFIG. TB1.

FIG. TB7 shows a side view of the input shaft of the input assembly ofFIG. TB1.

FIG. TB8 shows a front view of the input shaft of the input assembly ofFIG. TB1.

FIG. TB9 shows a view of the open side of the output engager of theinput assembly of FIG. TB1.

FIG. TB10 shows a perspective view of the input engager of the inputassembly of FIG. TB1.

FIG. TB11 shows a rear view of the input engager of the input assemblyof FIG. TB1.

FIG. TB12 shows a front view of the input engager of the input assemblyof FIG. TB1.

FIG. TB13 shows another perspective view of the input engager of theinput assembly of FIG. TB1.

FIG. TB14 shows a side view of the input engager of the input assemblyof FIG. TB1.

FIG. TB15 shows another side view of the output engager of the inputassembly of FIG. TB1.

FIG. TB16 shows an exploded view of the output assembly of Figure TB2.

FIG. TB17 shows a side view of the output shaft of the output assemblyof FIG. TB2.

FIG. TB18 shows a front view of the output shaft of the output assemblyof FIG. TB2.

FIG. TB19 shows a perspective view of the output engager of the outputassembly of FIG. TB2.

FIG. TB20 shows a cross-sectional view of the output engager of theoutput assembly of FIG. TB2.

FIG. TB21 shows front view of the output engager of the output assemblyof FIG. TB2.

FIG. TB22 shows another perspective view of the output engager of theoutput assembly of FIG. TB2.

FIG. TB23 shows a rear view of the output engager of the output assemblyof FIG. TB2.

FIG. TB24 shows an exploded view of the fixed assembly of Figure TB3.

FIG. TB25 shows an exploded view of the fixed assembly of Figure TB3from another perspective.

FIG. TB26 shows a perspective view of the fixed cylinder of the fixedassembly of FIG. TB3.

FIG. TB27 shows a side view of the fixed cylinder of the fixed assemblyof FIG. TB3.

FIG. TB28 shows a front view of the fixed cylinder of the fixed assemblyof FIG. TB3.

FIG. TB29 shows a perspective view of a spring used in theanti-backdrive mechanism of FIG. TB4.

FIG. TB30 shows a front view of the spring of FIG. TB29.

FIG. TB31 shows a side view of the spring of FIG. TB29.

FIG. TB32 shows a side of the nested input and output engagers with theoutput engager transparent so that the contours in the interior of theoutput engager can be seen along with the input engager and the springof FIG. TB29.

FIG. TB33 shows another side of the nested input and output engagerswith the output engager transparent so that the contours in the interiorof the output engager can be seen along with the input engager and thespring of FIG. TB29.

FIG. TA1 shows the input assembly of an anti-backdrive mechanism shownin FIG. TA4.

FIG. TA2 shows the output assembly of an anti-backdrive mechanism shownin FIG. TA4.

FIG. TA3 shows the fixed assembly of an anti-backdrive mechanism shownin FIG. TA4.

FIG. TA4 shows an anti-backdrive mechanism assembly incorporating theinput assembly of FIG. TA1, the output assembly of FIG. TA2 and thefixed assembly of FIG. TA3.

FIG. CL1 shows the input assembly of an anti-backdrive mechanism shownin FIG. CL4.

FIG. CL2 shows the output assembly of an anti-backdrive mechanism shownin FIG. CL4.

FIG. CL3 shows the fixed assembly of an anti-backdrive mechanism shownin FIG. CL4.

FIG. CL4 shows an anti-backdrive mechanism assembly incorporating theinput assembly of FIG. CL1, the output assembly of FIG. CL2 and thefixed assembly of FIG. CL3.

FIG. CL5 shows a top view of the anti-backdrive mechanism assembly ofFIG. CL4.

FIG. CL6 shows an exploded view of the input assembly of Figure CL1.

FIG. CL7 shows a cross-sectional view of the slotted plate of the inputassembly of FIG. CL8.

FIG. CL8 shows a front view of the slotted plate of the input assemblyof FIG. CL1.

FIG. CL9 shows a rear view of the slotted plate of the input assembly ofFIG. CL1.

FIG. CL10 shows an exploded view of the output assembly of Figure CL2.

FIG. CL11 shows an exploded view of the fixed assembly of FIG. CL3.

FIG. CL12 shows a perspective view of a rotating plate of the fixedassembly of FIG. CL3.

FIG. CL13 shows a top view of a rotating plate of the fixed assembly ofFIG. CL3.

FIG. CL14 shows a side view of a rotating plate of the fixed assembly ofFIG. CL3.

FIG. CW1 shows the input assembly of an anti-backdrive mechanism shownin FIG. CW4.

FIG. CW2 shows the output assembly of an anti-backdrive mechanism shownin FIG. CW4.

FIG. CW3 shows the fixed assembly of an anti-backdrive mechanism shownin FIG. CW4.

FIG. CW4 shows an anti-backdrive mechanism assembly incorporating theinput assembly of FIG. CW1, the output assembly of FIG. CW2 and thefixed assembly of FIG. CW3.

FIG. CW5 shows a top view of the anti-backdrive mechanism assembly ofFIG. CW4.

FIG. CW6 shows an exploded view of the input assembly of Figure CW1.

FIG. CW7 shows an exploded view of the output assembly of Figure CW2.

FIG. CW8 shows an exploded view of the fixed assembly of Figure CW3.

FIG. CW9 shows a front view of the slotted plate of the input assemblyof FIG. CW1.

FIG. CW10 shows a rear view of the slotted plate of the input assemblyof FIG. CW1.

FIG. CW11 shows a top view of the slotted plate of the input assembly ofFIG. CW1.

FIG. E1 shows a rack and pinion elevation mechanism mounted to aninternal saw structure.

FIG. E2 shows the rack and pinion elevation mechanism of FIG. E1isolated.

FIG. E3 shows a threaded rod and miter gear elevation mechanism mountedto an internal saw structure.

FIG. E4 shows the threaded rod and miter gear elevation mechanism ofFIG. E3 isolated.

FIG. E5 shows a belt operated elevation mechanism mounted to an internalsaw structure.

FIG. E6 shows the belt operated elevation mechanism of FIG. E5 isolated.

FIG. E7 shows a cable and threaded shaft elevation mechanism mounted toan internal saw structure.

FIG. E8 shows the cable and threaded shaft elevation mechanism of FIG.E7 isolated.

FIG. E9 shows the cable of the elevation mechanism of FIG. E7.

FIG. E10 shows a cable and spool elevation mechanism mounted to aninternal saw structure.

FIG. E11 shows another view of the cable and spool elevation mechanismof FIG. E10 mounted to an internal saw structure.

FIG. E12 shows the cable and spool elevation mechanism of FIG. E10isolated.

FIG. E13 shows a swinging arc sector and cable elevation mechanismmounted to an internal saw structure.

FIG. E14 shows the swinging arc sector and cable elevation mechanism ofFIG. E13 isolated.

FIG. E15 shows a worm and cable elevation mechanism mounted to aninternal saw structure.

FIG. E16 shows the worm and cable elevation mechanism of FIG. E15isolated.

FIG. E17 shows a lever elevation mechanism.

FIG. E18 shows an elevation limit stop installed on the input shaft towhich a handwheel is connected.

FIG. E19 shows an input shaft fully rotated clockwise and stopped fromfurther rotation by the limit stop of FIG. E18.

FIG. E20 shows an input shaft fully rotated counter-clockwise andstopped from further rotation by the limit stop of FIG. E18.

FIG. E21 shows a screw used to adjust the limit stop and to keep it fromrotating on the shaft?

FIG. E22 shows a perspective view of the limit stop of FIG. E18isolated.

FIG. E23 shows a front view of the limit stop of FIG. E18 isolated.

FIG. E24 shows a side view of the limit stop of FIG. E18 isolated.

FIG. E25 shows a top view of the limit stop of FIG. E18 isolated.

FIG. TF1 shows a tool used to assemble the anti-backdrive mechanismshown in FIGS. 3 through 38.

FIG. TF2 shows the tool of FIG. TF1 with part of the anti-backdrivemechanism in the tool.

FIG. TF3 shows the tool of FIG. TF1 with still more of theanti-backdrive mechanism in the tool.

FIG. TF4 shows the tool of FIG. TF1 with the assembled anti-backdrivemechanism.

FIG. TF5 shows the tool of FIG. TF1 with a flange plate, locking springsand locking cylinders installed.

FIG. TF6 shows the tool of FIG. TF5 with a release plate.

FIG. TF7 shows the assembled tool of FIG. TF1.

FIG. Z1 shows and embodiment of an elevation mechanism with an overloadshock absorber.

FIG. Z2 shows a cable used in the elevation mechanisms of FIG. Z1.

FIG. Z3 shows a cable around a spool in the elevation mechanism of FIG.Z1.

FIG. Z4 shows a locator or stop on the cable shown in FIG. Z3.

FIG. Z5 shows a bracket used in the elevation mechanism of FIG. Z1.

FIG. Z6 shows part of an overload shock absorber used in the elevationmechanism of FIG. Z1.

FIG. Z7 shows a shock plate.

FIG. Z8 shows an exploded view of components used in the elevationmechanism of FIG. Z1.

FIG. Z9 shows an input coupler used in the elevation mechanism of FIG.Z1.

FIG. Z10 shows a handwheel used in the elevation mechanism of FIG. Z1.

FIG. Z11 shows a handle body used in the handwheel of FIG. Z10.

DETAILED DESCRIPTION

FIG. 1 shows a table saw 10 including a table 12 and a circular blade 14extending up through a slot 16 in a table insert 18 that fits within anopening in the table. A piece of wood, or other material to be cut, isplaced on the table and pushed into contact with the spinning blade tomake a cut. The saw includes a motor and drive mechanism (not shown) tospin the blade. The blade may be raised or lowered to adjust to theheight of the workpiece by turning an elevation handwheel 20 thatextends out from the saw. (Typically in a table saw the blade may alsobe tilted relative to the table top to make an angled or bevel cut, andsaw 10 includes a handwheel 22 that can be rotated to tilt the bladefrom 0 to 45 degrees.)

Blade elevation mechanisms in table saws often use handwheels, mitergears (also known as bevel gears), and threaded shafts to raise or lowerthe blade. However, the threads on the shaft must be sufficientlyshallow to prevent the weight of the blade, along with the weight of themotor and any other structure being raised with the blade, from causingthe blade to fall back down when a user releases the handwheel. This iscalled “backdrive” because the weight of the structure turns the gearsor moves other components of the elevation mechanism in reverse anddrives the blade back down. A consequence of shallow threads, however,is that it takes many turns of the shaft (and therefore the handwheel)to raise and lower the blade. A user might have to turn the handwheel20, 30 or more times to raise or lower the blade. Alternatively,elevation mechanisms use worm gears or rack and pinion gears to raiseand lower the blade. Again in those systems, the weight of the blade,along with the weight of the motor and any other structure raised by theelevation mechanism, can cause the blade to move or fall back down whena user releases the handwheel.

Table saw 10 in FIG. 1 includes an elevation mechanism with ananti-backdrive device. The anti-backdrive device allows handwheel 20 todrive the elevation mechanism to raise or lower the blade, but theanti-backdrive device prevents the weight of the blade and otherstructure from turning, or back-driving, the elevation handwheel. As aresult, the elevation mechanism can be constructed so that a relativelyfew number of turns, a single turn, or even less than a single turn ofthe handwheel can fully raise or lower the blade. Various embodimentsand components of such an elevation mechanism are described below.

FIG. 2 shows elevation handwheel 20 mounted at the end of an input shaft24 that is connected to an anti-backdrive mechanism 26 which is in turnconnected to an output shaft 28 at the end of which is attached a cablepulley 30. The cable pulley 30, as will be described below, meshes witha cable or cables to raise and lower the blade when a user turnshandwheel 20. Input shaft 24 extends out from the interior of the saw toconnect to elevation handwheel 20 and turns or rotates as the elevationhandwheel is turned. The anti-backdrive mechanism 26 transmits theturning motion of the input shaft to output shaft 28 and cable pulley30. As the output shaft turns, the cable pulley turns and cables wind orunwind about the cable pulley to raise or lower the blade. Theanti-backdrive mechanism 26 allows the input shaft to turn the outputshaft, but prevents the output shaft from turning the input shaft. Moreprecisely, the anti-backdrive mechanism prevents both the output shaft28 and the input shaft 24 from turning under a torque applied to theoutput shaft, but allows both shafts to turn together either clockwiseor counter-clockwise when a torque is applied to the input shaft. Atorque may be applied to the output shaft by the weight of the structuresupporting the blade or by sudden movements of other structures internalto the saw. In any case, the anti-kickback mechanism will prevent suchtorques from turning either the output shaft or the input shaft so thatthe cable pulley does not turn and the blade will retain the setelevation.

The anti-backdrive mechanism 26 can be broken into three mainstructures: a release plate 40, a structure composed of a flange plate42 rigidly attached to a ramp plate 44, and a vertical plate 46. Asshown in FIG. 3, the release plate 40 is attached to the end of theinput shaft 24 and rotates as the input shaft and elevation handwheel 20rotate. The structure composed of the flange plate and ramp plate isattached to the end of the output shaft 28, as shown in FIG. 4, androtates as the output shaft and cable pulley rotate. The vertical plate46, shown in FIG. 5, supports the anti-backdrive mechanism in the saw,and is mounted in the saw so that it does not move with respect to othercomponents in the anti-backdrive mechanism.

As shown in FIG. 6, the anti-backdrive mechanism is assembled with thevertical plate 46 positioned in between the flange plate 42 and rampplate 44. The flange and ramp plates are centered about a large circularcutout 48 in the vertical plate through which pass two screws 50(identified in FIG. 33) that attach the flange and ramp plates together.Release plate 40 is positioned between vertical plate 46 and ramp plate44, and the input shaft 24, which is connected to the release plate,passes through a hole at the center of the ramp plate and extends outtowards the elevation handwheel.

FIGS. 7 through 11 show the release plate 40 isolated. Release plate 40is made of a rigid material such as metal or plastic and is generallyshaped like a rather thin plate with a circular middle section 52 andtwo wings, or arced sections 54, one extending out symmetrically to eachside beyond the radius of the circular middle section. Each arcedsection 54 sweeps through about ninety degrees. A short, hollowcylindrical extension 56 extends out from the center of the front sideof the release plate and has a hole 58 in the end running parallel tothe axis and two small holes 60, axially aligned with each other,passing through the sides of the cylindrical extension. The end of inputshaft 24 fits within hole 58 at the end of the cylindrical extension 56and a spring pin passes through aligned holes 60 and through a hole nearthe end of the input shaft to attach the release plate to the inputshaft. If the release plate is made of plastic, it may not be strongenough to accommodate the turning force, or torque, of the input shaftattached to the release plate by a spring-pin and so an alternativedesign, such as that shown in FIG. 12 may be used. This design uses aslightly modified release plate 66. Release plate 66 is substantiallythe same as release plate 40 except that the cylindrical extension onthe front of the release plate is modified. As shown in FIGS. 13 through16 the cylindrical extension 68 on the back side of the release plate iselongated a bit and has a small threaded hole 70 in the end runningparallel to and concentric with the axis. Chunks of the cylindricalextension cut longitudinally from the end of the cylindrical extensionto about half the length of the cylindrical extension and cut into thecylindrical extension following radial lines for a depth of about halfthe radius of the cylindrical extension are removed along thecircumference of the cylindrical extension 68 leaving six equally sizedand spaced remnants 72 that are about one half as wide as the removedchunks alternating with six equally spaced gaps 74 to create a splinetype of interface. The cylindrical extension interlocks with acorresponding piece called a coupler 76, shown isolated in FIGS. 17through 20, which has a matching six segment pattern with the chunks cutinto the inner surface of the hollow, cylindrical end of the coupler sothat the coupler can fit over the end of the cylindrical extension. Thecoupler 76 is attached to the cylindrical extension by a screw 78 whichpasses through a hole 80 in a thick wall 82 which runs perpendicular tothe longitudinal axis of the coupler and located at about the middle ofthe coupler. The back of the head of screw 78 lies against wall 82 andthe end threads into hole 70 at the end of the cylinder extension 68.The coupler couples the release plate to the input shaft to provide moresurface over which to spread the rotating force upon the cylindricalextension of the release plate thus reducing pressure points that maylead to damage. The front end of the coupler opposite the patterned endis shaped such that the coupler narrows to form a circular opening of asmaller diameter while it also closes, or pinches, in on the sides toform a pocket 84 that has a circular opening in the center which opensinto rectangular shaped openings on the sides. The pocket 84 extendsinto the interior of the coupler for about half the length of thecoupler. The end of an input shaft 86 fits within the circular centerand the two ends of a spring pin 88 which passes through a hole 90 nearthe end of the input shaft fit within the rectangular sides. The springpin pushes on the interior surfaces of the coupler to transfer theturning motion of the input shaft to the coupler which then transmitsthe turning motion to the release plate. Because the coupler is notrigidly attached to the input shaft, the input shaft is kept fromsliding out of the end of the coupler by an E-clip that fits in a groove92 around the input shaft and abuts the side of a washer that liesagainst an extension from the internal saw structure which has a hole init for the input shaft to pass through to mount the input shaft in thesaw.

On the face of release plate 40 opposite the face attached to the inputshaft, there is a raised rim 94 along the outer edge of each of the sidearced sections, as shown in FIGS. 8 and 10, which continues a shortdistance radially inward at each end. The rims add strength to therelease plate and also serve as a standoff reducing the contact areabetween the release plate and the vertical plate to minimize thefriction that arises when the release plate rotates with respect to thevertical plate. Also on the face of the release plate opposite the faceattached to the input shaft, there is a small solid cylindricalprojection 96 that extends out from the center of the face and issurrounded by a wall 98 that circles around and encloses most of thecylindrical projection except for an opening 100 to one side, as shownin FIGS. 8 and 10. The coil at the center of a torsion spring 102 fitsaround the cylindrical projection 96 and within wall surrounding thecylindrical projection, as shown in FIG. 21. Torsion spring 102, shownisolated in FIGS. 22 through 24, is generally shaped like a coil 104with two straight segments 106, one segment continuing out from each endof the coil, extending out in opposite directions along lines parallelto each other and set apart by the height of the coil in a planeperpendicular to the circular face of the coil. When looking down on thecircular face of the coil the two straight segments appear to form astraight line tangent to the coil, as shown in FIG. 23. The end 108 ofeach straight segment is bent ninety degrees towards the opposite end ofthe coil and along lines parallel to the axis going through the centerof the coil. One straight side segment of the torsion spring lies alongthe surface of the release plate and passes through opening 100 in thewall 98. The other straight side segment of the torsion spring exits theother end of the coil and lies along the surface of the flange plate 42with the bent end 108 of the torsion spring, which appears on the rightside when looking at the face of the release plate containing torsionspring 102 oriented such that the straight segments 106 run horizontallybelow the coil 104, reaching back towards the release plate where itfits into a generally rectangular recessed area 110 on the release platesurrounded by a wall 112. A spacer structure 114 in the shape of a thin,arced segment projecting outward from the face of the release platecontacts the underside of the straight side segment of the torsionspring leading to the rectangular area 110 to keep the tip of the springfrom digging into the release plate at the bottom of the rectangularrecessed area. The wall 98 about the cylindrical projection 96 continuesout from the center of the release plate and forms a triangularenclosure around a triangular recessed area 116 into which opening 100spills into, and which appears on the left side opposite the rectangularrecessed area 110 when looking at the face of the release platecontaining torsion spring 102 oriented such that the straight segments106 run horizontally below the coil 104. The straight segment 106 of thetorsion spring that lies along the release plate is situated within thetriangular area 116 and can move within this area as the release platerotates relative to the flange plate. The triangular area is notcompletely enclosed but the wall 98 around the area is interrupted onthe top and bottom sides by short breaks 118 deep enough to allow aspacer structure 115, similar to spacer 114 on the release plate butextending outward from the inner surface of the flange plate towards therelease plate, to pass through as the release plate rotates with respectto the flange plate. The front of the release plate is not entirely flataround the cylindrical extension 56 to which the input shaft attachesbut rather is raised in the region corresponding to the circular area 52at the center of the release plate and to the triangular and rectangularareas 116 and 110 on the other side of the release plate. This raisedsurface 120 has the shape of a circular area with two small wingedsections that extend out to either side as far as the triangular andrectangular areas extend and will be used to help keep the release plateoriented with respect to the ramp plate as will be discussed later.

Flange plate 42, shown isolated in FIGS. 25 through 28, is generallyshaped like a circular plate with a hollow cylindrical extension 122with thick sides extending out from around the center of the rear face.Cylindrical extension 122 fits over output shaft 28 and is held in placeby a spring pin which passes through a hole 126 in the side of thecylindrical extension 122, then through a hole near the end of theoutput shaft and then through another hole 126 in the cylindricalextension directly across from the first hole in the cylindricalextension. The front face of flange plate 42 is recessed along the outeredge to create a narrow surface 130 around the circumference of theplate against which the vertical plate lies while the remainingnon-recessed surface 132 of the flange plate passes through the largecircular cutout 48 in the vertical plate and protrudes out just a bitbeyond the vertical plate. A cylindrically shaped recessed area 134 atthe center of the front face of flange plate 42 fits over and surroundsthe coil of torsion spring 102. Regions 111 and 117, corresponding tothe shaped rectangular and triangular areas 110 and 116 found for thetorsion spring on the release plate, are carved into the front face ofthe flange plate and the release and flange plates are arranged so thatwhen they are put together the rectangular area 110 on the release plateis across from the triangular area 117 on the flange plate while thetriangular area 116 on the release plate is across from the rectangulararea 111 on the flange plate. As with the triangular region on therelease plate, the border along the triangular region on the flangeplate is not continuous but is interrupted by breaks 119 along the topand bottom which provide clearance for the spacer structure 114 on therelease plate so the release plate may rotate with respect to the flangeplate. Unlike the torsion spring pattern on the release plate there areno raised rims about the rectangular or triangular regions on the flangeplate but rather they are recessed areas.

As the elevation handwheel 20 first begins to rotate clockwise, therelease plate 40 begins to rotate clockwise while the flange plateremains stationary momentarily and the inside wall of the triangulararea 116 on the release plate pushes one end of the torsion spring 102while the other end of the torsion spring is held in place by pressingagainst the inside wall of the triangular area on the flange plate. Thusthe torsion spring 102 deforms, or bends, as the release plate rotateswith respect to ramp plate 44, that is, as one end of the spring movesrelative to the other end. As the release plate rotatescounter-clockwise the situation is reversed and the opposite end of thespring is pushed by the inside wall of the rectangular area 110 on therelease plate while the other end of the spring is held in place bypressing against the inside wall of the rectangular area on the flangeplate. Again the torsion spring deforms as one end moves relative to theother end. The triangular areas are shaped to accommodate the movementof the entire length of the straight segments of the torsion spring, oneof which lies against the surface of the flange plate and the otheragainst the release plate, whereas the rectangular areas need onlyaccommodate the bent ends of the torsion spring. Once the flange platebegins turning, both the input and output shafts turn, and the torsionspring remains in a bent configuration due to the drag on the flangeplate from the rest of the saw. Only when the elevation handwheel 20 isreleased does the torsion spring straighten out again resetting therelease plate back to its default position with respect to the flangeplate.

On the front face of the flange plate, which faces the release plate,there are two pairs of cylindrical projections 136 set at equaldistances from the center of the plate, one located just above thecylindrical recessed area 134 that surrounds the coil of the torsionspring at the center of the flange plate and one pair below thecylindrical recessed area. Each pair is situated such that a linerunning through the center of each cylindrical projection in one pairwould be parallel to a line running through the straight segments of thetorsion spring. A locking spring 138, shaped like two small loopssituated side-by-side with a straight segment exiting each loop, fitsaround each pair of cylindrical projections, one locking spring for eachpair of cylindrical projections, as shown in FIG. 29. Locking spring 138is shown isolated in FIGS. 30 through 32. The two small loops of thelocking spring 138 are the same size and are positioned side by side insuch a way that the axis through each loop is parallel to each other andseparated by a distance that is only slightly larger than the diameterof each loop. The straight segments exit each loop at about a sixtydegree outward angle so that an angle of about 120 degrees is formedbetween them. As mentioned, the two loops in the locking spring fit overthe two cylindrical projections 136 and the straight segments extendjust a bit past the outer edge of the flange plate. Over the end of eachstraight segment of each locking spring is placed a small lockingcylinder 140 cylindrically shaped with a hole running axially throughits length large enough for the straight ends of the locking spring tofit through loosely. The four locking cylinders are held in place bybeing trapped between the vertical plate and arced recessed areas 146 inramp plate 44, as can be seen in FIG. 33 and FIG. 34, that follow thearc of the outer edge of the ramp plate. One locking cylinder is trappedwithin each arced recessed area 146 such that the long side of eachcylinder lies against the ramp plate 44 but is allowed to move, or roll,along in an arc just within the outer rim of the ramp plate when pushedby the surfaces 152 along the edge of the winged sections of releaseplate 40. Four narrow, raised curved sections 154 on flange plate 42 arepositioned under each straight segment of the locking spring just belowthe bottoms of the locking cylinders and cover a width that the springstretches apart to each side to help keep the spring in position. Thereare four generally triangular recessed areas 156 carved into the flangeplate, one in each corner just inside the raised curved sections 154, tohelp maintain the flatness of the flange plate during the manufacturingprocess by keeping a more consistent wall thickness. The flange plate 42is attached to the ramp plate 44 by the two screws 50 which pass throughlocking washers 158 and then through bosses 142 in the ramp plate andscrew into threaded holes 144 in the flange plate, one located towardsthe top and one towards the bottom of the flange plate. The screws aresituated in such a way that a line joining both screws 50 runsperpendicular to a line running through the straight segments of thetorsion spring when the torsion spring is not bent. The bosses on theramp plate abut the flange plate and set the distance between the rampplate and the flange plate.

FIGS. 34 through 38 show ramp plate 44 isolated. Ramp plate 44 isgenerally shaped like a sided circular plate with a hole 160 in thecenter through which passes the cylindrical extension 56 on the releaseplate that surrounds the input shaft 24, and two small holes 162, oneabove the center hole 160 and one below for screws 50 that attach theramp plate to the flange plate. The front face of the ramp plate is flatas well as a narrow surface 168 along the outermost edge of the rearface of the ramp plate. The outer side surface 164 around the ramp plateis also flat except for a rim 166 along the rear edge of the outersurface which extends radially outward a bit beyond the outer sidesurface to form a peak or ridge 170. A foam filter 172, shaped like aflat ring lies along the outer edge of the ramp plate between thevertical plate and the ridge 170, as shown in FIG. 39, to seal theinterior of the anti-backdrive mechanism from dust. The part of the rampplate that presses against the foam filter is peaked in order tominimize friction as the ramp plate turns. Instead of the foam filter adust cover 180 may be placed over the ramp plate and secured to thevertical plate to help keep dust out of the anti-backdrive mechanism asshown in FIG. 40. Dust cover 180, shown isolated in FIGS. 41 and 42, isshaped like a circular cover with three bosses which are equally spacedalong the outside perimeter of the cover and which each have a threadedhole. A screw passes through each threaded hole to attach the cover tothe vertical plate. The surface along the edge of the dust cover is flatin order to lie flat up against the vertical plate to help keep the dustout. As shown in FIG. 39, a second smaller flat, ring-shaped filter 178may be added on the front face of the ramp plate surrounding thecylindrical extension 56 of the release plate to help seal the interiorof the anti-backdrive mechanism from dust.

Around the center of the inside face of the ramp plate there is arecessed area 174 shaped like a circle with radial sweeps to each sideinto which fits the correspondingly shaped raised area 120 on the frontof the release plate with a little extra room to accommodate a slightrotation of the released plate. As mentioned earlier, raised area 120fitted within recessed area 174 helps to keep the release plate orientedwith respect to the ramp plate such that the release plate may rotateabout 8 degrees in either direction from a centered position relative tothe ramp plate. On the inside face of the ramp plate just beyond eachscrew 50 and between each arced recessed area 146 that run along theouter rim of the ramp plate there are two generally triangular-shapedraised areas that function as stops 176. The outer edge of the stopsfollow the arc of the outer rim of the ramp plate and the sides of stops176 follow radial lines moving inward which give them their triangularshape though the stops end before the radial lines intersect so that thetip of the triangle is clipped. The surface along the arced recessedareas 146 on either side of each stop starts with a level rectangularsurface 148 near each side of each stop followed by a ramped surface 150that ramps up to a higher level surface moving away from the stop ineither direction, as shown in the cross-sectional view in FIG. 38. Thedifference between the level of the surface in the arced recessed areasand the adjoining non-recessed surface forms a boundary that helps keepsthe locking cylinders confined to the arced recessed area.

The default state of the anti-backdrive mechanism occurs when there isno torque being applied to the elevation handwheel. In the default statethe locking cylinders within each pair are forced apart from each otherby the locking spring 138 to which they are linked and rest upon theramped surfaces 150 of the arced recessed areas about half way up theramp where they become wedged between the bottom surface of the ramp andthe vertical plate 46. Also in the default state, torsion spring 102keeps the release plate oriented symmetrically about a straight linepassing through the two screws 50 and the hole 160 in the center of theramp plate. If a torque is applied to output shaft 28 while theanti-backdrive mechanism is in the default state, the ramp plate willstart to turn and two of the locking cylinders 140 will try to movefarther up the ramp more strongly wedging the cylinders between thevertical plate and the ramp plate. If the output shaft turns clockwisethe upper, left cylinder (when seen from the front of the saw) and thelower, right cylinder will become more strongly wedged. If the outputshaft is turned counter-clockwise the other two cylinders will becomemore strongly wedged. This prevents the ramp plate and thus both theinput and output shafts from rotating under the torque applied to theoutput shaft.

Turning the elevation handwheel 20 releases the anti-backdrive mechanismfrom the default state. As the input shaft turns, the release plateattached to the end of the input shaft rotates and contacts two of thelocking cylinders dislodging them by pushing them down their ramps andagainst stops 176 which transfers the rotating motion to the ramp plateand to the output shaft attached to the ramp plate. When the elevationhandwheel is turned clockwise, the input shaft turns clockwise and thecylinders that are dislodged are the upper-left cylinder and thelower-right cylinder (when seen from the front of the saw). The othertwo cylinders simply move down their ramps toward the stops as the rampplate turns so that they do not interfere with the rotating motion. Whenelevation handwheel 20 is turned counter-clockwise, the upper-right andbottom-left cylinders are pushed toward stops and the other twocylinders move down their ramps toward the stops as the ramp platerotates. When the elevation handwheel is released, the torsion spring102 pulls the release plate back to the default position relative to theramp plate and the locking springs push the locking cylinders 140 up theramps until they are again wedged between the vertical plate and theramp plate. A distance is kept between each locking cylinder and theedge of the release plate near each locking cylinder to keep the releaseplate from accidently hitting the locking cylinders and releasing theanti-backdrive mechanism from the locked state when the elevationhandwheel is bumped or when there is vibration or other unintendedmovement that might cause the input shaft to rotate slightly.

As the elevation handwheel is turned, the output shaft 28 turns alongwith the cable pulley attached to the end of the output shaft and cableswind or unwind to change the elevation of the blade support structureand blade. There are two cables 182 and 184 attached to cable pulley 30.Cable 182 is attached to cable pulley 30 at one end, winds clockwiseabout cable pulley and then extends vertically upward and attaches atthe other end to the top of blade support structure 186. The othercable, cable 184, is attached to cable pulley 30 at one end, windscounter-clockwise about the cable pulley and then extends verticallydownward and attaches at the other end to the bottom of the bladesupport structure 186. When the elevation handwheel 20 is turnedclockwise, the cable pulley turns clockwise and cable 182 unwinds whilecable 184 winds, thus pulling the bottom of the blade support structureupward and raising the blade. When the elevation handwheel 20 is turnedcounter-clockwise, the cable pulley turns counter-clockwise and cable182 winds while cable 184 unwinds allowing the bottom of the bladesupport structure 186 to move down and lower the blade. Whether theelevation handwheel is turned clockwise or counter-clockwise, it is thebottom cable 184 which raises or lowers the blade against the downwardforce of gravity and any unexpected downward force that might arise andwould need to be counteracted while the upper cable follows the motionand helps to keep the blade at the set elevation in the case an upwardforce might arise which would need to be counteracted. A gas spring maybe installed in the saw to counteract the downward force of gravity thusallowing the elevation handwheel to be turned more easily and with amore consistent feel whether turning the handle clockwise orcounter-clockwise.

Gears could be used to implement the elevation mechanism instead ofcables but cables provide some benefits different than gears. Forexample, cables absorb vibration, they provide a smooth feel as theoperator turns the handle to raise or lower the blade, and dust is lesslikely to build up on cables and degrade performance as often happenswith gears. An elevation mechanism using a cable pulley is one type ofelevation mechanism, alternative types of elevation mechanisms arediscussed below.

FIGS. S1 through S21 show another design for an anti-backdrive mechanism200 this time incorporating a spring lock. Once again the overallassembly is composed of three main sub-assemblies that move relative toone another: an input shaft assembly 202 shown in FIG. S1, an outputshaft assembly 204 shown in FIG. S2 and a fixed assembly 206 shown inFIG. S3. The complete assembly incorporating a spring-lockanti-backdrive mechanism is shown in FIG. S4.

The input assembly 202 includes an input shaft 208 attached to an inputarm 210. Input shaft 208, shown isolated in FIG. S5, is shaped like asolid cylindrical rod with portions cut out longitudinally at each endso to create flat rectangular surfaces 212 and 214 that lie parallel toeach other. At one end 216 of the shaft the portion cut away from theshaft to form flat surface 212 runs about as deep as one-eighth of thediameter of the shaft. This end 216 also has a hole 217 running throughit along the axis and is used to mount the handwheel 20. A greaterportion is cut away at the other end 218 of the shaft running about asdeep as one-quarter the diameter of the shaft to form flat surface 214.This end 218 fits into input arm 210, shown isolated in FIGS. S6 and S7.Input arm 210 has a cylindrical section 220 shaped like a hollowcylinder which is followed by a solid semicircular section 222 of nearlyequal length that extends out lengthwise, concentric with cylindricalsection 220, and is shaped like a solid cylinder cut straight along itslength a bit below the diameter so that the semicircular section is lessthan half of a solid cylinder and has a flat surface 224 the edges alongeach side of which are rounded. Input arm 210 fits over the end section218 of the input shaft and is secured by a set screw 226 which passesthrough a hole 228 on the side of the cylindrical section of the inputarm and contacts the flat surface 214 at the end of the input shaft. Atorsion spring 230 is placed over the semicircular end of the input arm210, as shown in FIG. S1. Torsion spring 230, shown isolated in FIG. S8,is shaped like a coil with the ends 231 bent directly inward alongradial lines toward the axis of the coil from opposite sides of the coiland opposite ends of the coil such that both straight ends are parallelto each other and also parallel to planes that run perpendicular to theaxis through the coil, and both straight ends lie in a common planewhich runs along the axis of the coil. The bent ends wrap around therounded corners and lie over and parallel to the flat surface 224 of theinput arm, as shown in FIG. 81. The output shaft assembly, shown in FIG.S2, is similar to the input shaft assembly with an output shaft 232,shown isolated in FIG. S9, that has a portion cut away at one end likeend 218 of the input shaft over which is placed an output arm 234 shapedsimilarly to the input arm 210 except that the output arm 234 hascornered edges along the sides of the semicircular section instead ofrounded edges as can be seen in FIG. S10. The length of the semicircularsection of the output arm is the same as the length of the semicircularsection of the input arm. The end of the output shaft 232 opposite theend that attaches to the output arm will have a configuration suitablefor the specific design of the elevation mechanism to which it would beattached.

FIG. S3 shows fixed assembly 206 which consists of a mounting block 236that supports a split cylinder 238 which is surrounded at one end by ahose clamp 240. Mounting block 236, shown isolated in FIG. S11, isshaped like a narrow rectangular block, vertically oriented, with twosmall holes 242 located near the middle of the block, one above theother, a large hole 244 located towards the bottom of the mounting blockand a small hole 246 which comes up from the bottom edge of the blockand passes through to the large hole 244. Small holes 242 are used forscrews that rigidly attach the block to the internal structure of thesaw. The large hole 244 is used to mount the split cylinder 238. Splitcylinder 238, shown isolated in FIGS. S12 through S13, is shaped like ahollow cylinder split into three sections. One endsection 248 is shapedlike a hollow cylinder of about half the diameter and about one-fifththe length of the entire split cylinder and which is flattened along oneside to create a flat surface 250. The end section 248 of the splitcylinder fits within large hole 244 located towards the bottom of themounting block 236. The split cylinder is rigidly attached to themounting block by a set screw 252 which passes through hole 246 in thebottom edge of the mounting block and presses against the flat surface250 of the short end section of the split cylinder. The other twosections 256 and 258 of the split cylinder are of the same diameter andnearly equal length with the cylindrical section 256 at the end of thesplit cylinder being slightly shorter in length than section 258. A gap254 separates the two cylindrical sections 256 and 258. Gap 254 runsperpendicular to the axis of the split cylinder and goes almost all theway through the split cylinder leaving only a small portion of less thanone-eighth the diameter of the cylinder intact. Another narrow segmentis cut out along the top of the shorter section 256 running along thelength of the section forming a gap 260 that allows the sides of section256 to be squeezed together, as shown in FIG. S12. Hose clamp 240, shownisolated in FIG. S15, is placed over section 256, as shown in FIG. S16,so that the inner diameter of the section 256 may effectively bereduced.

The anti-backdrive mechanism is assembled with the input and outputshafts aligned concentrically and the output arm 234 positioned abovethe input arm 208 so that the flat surfaces of each arm face each otherbut are separated by a gap. The output arm fits within the torsionspring 230 above the two ends of the torsion spring that are wrappedaround the input arm 208 so that the torsion spring encompasses the twoarms, as shown in FIG. S17. The input and output assemblies 202 and 204are positioned in the fixed assembly 206 with the longer section 258 ofthe split cylinder overlapping the cylindrical portion of the input armand section 256 with the gap along the top overlapping the torsionspring as shown in FIGS. S16 and S17. To compensate for manufacturingvariations in the fabrication of the spring the adjustable hose clamp240 is placed around the spring and is adjusted to align the two ends ofthe spring along the same line so that there is some room for the inputand output arms to rotate enough in each direction to effectively deformthe spring. The natural diameter of the torsion spring is made slightlylarger than the split cylinder so that the spring presses firmly againstthe inner surface of the split cylinder when the spring is encased inthe split cylinder. This keeps the spring in firmly in place.

When the output shaft 232 starts to rotate, the output arm 234 rotatesand presses against one end of the torsion spring. The torsion spring iswound in such a way that each end starts parallel to the flat surface ofthe output arm and then turns away from the output arm, as shown inFIGS. S18 and S19, so the torsion spring will tend to increase indiameter near the end of the torsion spring that the output arm pressesagainst, as shown in FIG. S20. However, the torsion spring is preventedfrom increasing its diameter because it is already pressing up againstthe inner surface of the split cylinder so the torsion spring pressesagainst the spilt cylinder even more increasing its resistance frombeing turned relative to the split cylinder. Ideally, the torsion springwould be made of square wire that is wound into a coil as this wouldincrease the surface area of the spring that is in contact with theinner surface of the split cylinder thereby increasing the frictionbetween the spring and the split cylinder making the spring difficult toturn. When the output shaft is turned in the opposite direction itpresses against the other end of the spring but with the same result.Thus the output shaft is prevented from rotating in either directionwhen a torque is applied to the output shaft. As described earlier, atorque on the output shaft may arise from the load of the blade andblade elevation support structure on the elevation mechanism attached tothe end of the output shaft.

As the input shaft rotates, input arm 210 rotates and presses on one endof torsion spring 230. Recall that the torsion spring is wound in such away that it starts parallel to the flat surface of the input arm andthen curls around the curved surface of the semicircular section of theinput arm and then the end of the spring folds over the edge of theinput arm and extends over the flat surface so that when the input armrotates it pulls the end of the spring in the direction that the springis wound thus decreasing the diameter of the spring, as shown in FIG.S21. The diameter of the spring is most greatly decreased at the end ofthe spring that the input arm is pushing against and then less and lessso moving toward the other end of the coil. The decrease in the diameterof the spring reduces the force of the spring against the inner surfaceof the split cylinder which reduces the friction thus allowing thespring and input arm to rotate together within the split cylinder. Therewill be a certain level of frictional drag arising from the portion ofthe spring that still has a larger diameter but this drag is easilyovercome by the torque applied to the input shaft through the handwheel.The output arm which is confined within the spring is forced to rotateas the input shaft rotates and presses against the spring which thenpresses against the edge of the output arm causing the output shaft toturn. When the input shaft is turned in the opposite direction itpresses against the other end of the spring with the same result. Thus,both the input and output shafts rotate as the handwheel rotates ineither direction.

FIGS. U1 through U18 show another variation of an anti-backdrivemechanism 300 using a spring lock. Once again the overall assembly iscomposed of three main sub-assemblies: an input shaft assembly 302 shownin FIG. U1, an output shaft assembly 304 shown in FIG. U2 and a fixedassembly 306 shown in FIG. U3. The complete assembly incorporating aspring-lock anti-backdrive mechanism is shown in FIG. U4.

Anti-backdrive mechanism 300 uses a spring 308 shaped like a coil 310with the two ends 312 exiting outward from the coil on opposite sides ofthe coil, as shown in FIGS. U5, U6 and U7. Each spring end 312 consistsof a short, straight segment that exits the coil at an angle of a littleover ninety degrees with the winding leading to the spring end. An angleof over ninety degrees helps to strengthen the spring againstdeformations as a force is applied repeatedly to the ends of the springand more effectively transfers the force tending to unwind the coil. Asshown in FIG. U5, which is an exploded view of the fixed assembly 306,spring 308 fits around a cylinder 314 which is fixed to the sawstructure. Spring 308 is confined to an area along the cylinder by twoE-clips 316, one placed in each of two grooves 317 on the fixed cylindernear each end of the coil so that the space between the E-clips is justslightly larger than the length of the coil. Cylinder 314 passes througha large hole 318 near the top end of a mounting block 320 which also hasa small threaded hole 322 drilled into the top edge of the mountingblock down toward the large hole 318 through which cylinder 314 passesand in which a set screw 324 is installed, the bottom of which makescontact with the outer surface of cylinder 314 to keep the cylinder frommoving. The mounting block 320 also has two threaded holes 325 alignedone above the other along the centerline of the mounting block near themiddle of the mounting block through which pass screws to rigidly mountthe mounting block to the internal structure of the saw. Thus the fixedcylinder 314 and mounting block 320, being rigidly attached to theinternal saw structure, do not move relative to the other components ofthe anti-backdrive mechanism.

The input shaft assembly, shown in FIG. U8, consists of input shaft 326attached to an input engager 332 which fits over the end of the inputshaft. Input engager 332, shown isolated in FIGS. U9 through U11, isshaped like a cylinder first cut lengthwise in half and then cut at anangle lengthwise along each side starting from near the bottom of thesame end and continuing near or just past the middle of the length ofthe cylinder until the angled cuts 334 and 336 on each side meethorizontal cuts 337 along which the cylinder was cut in half lengthwise.One side angled cut 334 continues for about half the length of thehalf-cylinder and the angled cut 336 on the other side continues forabout two thirds the length of the half-cylinder, as can best be seen inFIG. U10. The remainder of each side is cut horizontally forming twohorizontal surfaces 338 at the end of the half-cylinder that are on thesame plane. At the end of the input engager, spanning the gap betweenand rising above the horizontal surfaces 338, there is a thick wall 340that is generally circular in shape and vertically oriented, and has alarge hole 342 that is aligned coaxially with the cylinder. The wall 340continues above the sides of the half-cylinder but stays within a radiusa little smaller than the radius of the half-cylinder. A small threadedhole 344 passes through the bottom side of the half-cylinder underneathwall 340 and empties into the large hole 342 in wall 340. The inputshaft 326 is inserted into the large hole 342 in wall 340 and a setscrew 346 is installed in the threaded hole 344 along the bottom side ofthe input engager so that the bottom of the set screw makes firm contactwith the side of the input shaft to rigidly attach the input engager tothe input shaft. Input shaft 326 of the input assembly 302 passesthrough the interior of cylinder 314 in such a way that it is free torotate within the cylinder. Two E-clips 328 fit into grooves 330 on theinput shaft, one on each side of the cylinder, to fix the relativepositions of the cylinder to the input shaft.

The output shaft assembly 304, shown as an exploded view in FIG. U12,consists of an output shaft 348 attached to an output engager 350 whichfits over the end of the output shaft. Output engager 350, shownisolated in FIGS. U13 though U15, is shaped mostly like a cylinder withone end that is left open and one end that is closed except for a largehole 352 aligned coaxially with the cylinder. At the open end, thecylinder is cut horizontally for a short distance along each side justbelow a plane longitudinally cutting the cylinder in half so that theportion that is removed at the end is less than the portion that remainsat the end. As shown in FIG. U14, the horizontal cuts continue for aboutone-fourth the length of the cylinder, with the horizontal cut 354 onone side of the cylinder, the right side when looking directly at theopen end of the cylinder, slightly longer than the cut 356 on the otherside, at which point the cuts continues at an angle up to and about halfa radius past the plane longitudinally cutting the cylinder lengthwise.Horizontal cut 354 leads into angle cut 358 and the longer horizontalcut 356 leads into angle cut 360. The angled cuts 358 and 360 continuefor about another one-fourth of the length of the cylinder after whichthe cuts becomes horizontal again for about another one-fourth of thelength of the cylinder. The last one-fourth of the cylinder, or actuallyslightly more than one-fourth, is completely cylindrical to the closedend. The angled cuts 358 and 360 on the output engager are cut at thesame angle as the angled cuts 334 and 336 on the input engager so thatthey lie parallel to each other with a gap in between when the mechanismis assembled. The output shaft 348 is inserted into the large hole 352at the end of the output engager and a set screw 362 is installed in athreaded hole 364 along the side of the output engager that empties intothe large hole 352 so that the bottom of the set screw makes firmcontact with the side of the output shaft to rigidly attach the outputengager to the output shaft. Another hole 366 passes through the side ofthe output engager near the open end and a screw 368 passes through thishole and threads into a threaded hole 369 in a collar 370 which is likea large metal ring that surrounds the fixed cylinder 314 seated on theinput shaft and supports the end of the output engager by keeping itpositioned coaxially with the input shaft while allowing the outputengager to rotate freely around the fixed cylinder.

The anti-backdrive mechanism is assembled with the input and outputshafts 326 and 348 arranged concentrically and with the output engager350 interlaid with the input engager 332 so that the spring 308 issurrounded and angled sides 334 and 336 on the input engager face andare parallel to the angled sides 358 and 360 on the output engager witha gap in between through which extend the ends of spring 308, one endextending out through each side and slanting slightly toward the inputengager, as shown in FIGS. U16 through U18. A gap is left between thecollar 370 and the end of the input engager 332 to provide clearance.

As the input shaft 326 rotates one of the angled cuts 334 and 336 of theinput engager 332 hits an end 312 of the spring 308 and pushes it in thedirection of, or towards the last winding of the spring as if to unwindthe spring so that the spring expands increasing in diameter mostgreatly near the end of the spring that is being pushed and less andless moving towards the other end of the spring. When the diameter ofthe spring 308 increases, the spring loosens so that it turns about thefixed cylinder 314 as the input shaft rotates with a frictional dragthat is easily overcome by the torque applied in the input shaft throughthe handwheel. When the input shaft rotates in the other direction, theangled cut on the other side of the input shaft contacts the other end312 of the spring 308 which again loosens the spring so that it is freeto rotate. Thus, both the input and output shaft rotate as the handwheelrotates in either direction.

A different situation arises as the output shaft rotates. In this case,an angled cut 358 or 360 of the output engager 350 hits an end 312 ofthe spring 308 and pushes it in the direction of the spring windingwhich tends to tighten the spring around the fixed cylinder preventingthe output shaft from rotating. When the output shaft rotates in theother direction the angled cut on the other side of the output shaftcontracts the other end of the spring 308 which again tightens thespring preventing the shaft from rotating. Thus, neither the outputshaft nor the input shaft is able to rotate when a torque is applied tothe output shaft.

FIGS. B1 through B22 show another design for an anti-backdrive mechanism400 built around two metal plates situated in a set of threeconcentrically nested metal cylinders. Once again the overall assemblyis composed of three main sub-assemblies: an input shaft assembly 402shown in FIG. B1, an output shaft assembly 404 shown in FIG. B2 and afixed assembly 406 shown in FIG. B3. The complete assembly incorporatinganti-backdrive mechanism 400 is shown in FIG. B4.

FIG. B5 shows an exploded view of the input assembly 402 which consistsof a cylindrical input hinge 408 attached to an input shaft 410 by aspring pin 412. The input hinge 408 is the middle cylinder of the threenested cylinders in the anti-backdrive assembly and is shaped like ahollow cylinder that has two wide equally sized slots 414 with roundedcorners that run longitudinally along the side of the cylinder for abouttwo-thirds of the length of the cylinder and are positioned directlyacross from each other. The input shaft 410 is shaped like a rod with ashort, larger diameter section 415 at the end that fits within one endof the input hinge. The slots in the input hinge do not overlap the lastone-third of the length of the hinge where the larger diameter section415 at the end of the input shaft is inserted into the input hinge.Spring pin 412 passes through a small oval hole 416 on one side of theinput hinge 408 and then through a hole 418 through the larger diametersection 415 at the end of the input shaft end then through another smalloval hole 416 in the input hinge to secure the input hinge 408 to theinput shaft 410.

FIG. B10 shows an exploded view of the output assembly 404 whichconsists of a cylindrical output hinge 420, shown isolated in FIG. B11through B14, attached to an output shaft 422 by a spring pin 424. Theoutput hinge 420 is the innermost cylinder of the three nested cylindersin the anti-backdrive mechanism and is shaped like a hollow cylinderthat has two long slots with rounded corners in it, a narrow slot 426and a wide slot 428, that run longitudinally along the side of thecylindrical output hinge for about two thirds of the length of the hingestarting from near one end of the hinge. Slots 426 and 428 arepositioned across from each other so that the center lines runninglongitudinally though each slot share the same plane. The wide slot 428in the output hinge is slightly wider than the wide slots 414 in theinput hinge. The output shaft is shaped like a rod with a short largerdiameter section 429 at the end that fits within the end of the outputhinge. Like the input hinge, the slots in the output hinge do notoverlap the last one-third of the length of the hinge where the largerdiameter section 429 at the end of the output shaft is inserted into theoutput hinge. Spring pin 424 passes through a small oval hole 430 on oneside of the output hinge 420 and then through a hole 432 through thelarger diameter section 429 at the end of the output shaft and thenthrough another small oval hole 430 in the output hinge 420 to securethe output hinge to the output shaft 422. Two square metal plates 434,shown isolated in FIGS. B15 and B16, are set within the output hingewith one end of each plate protruding out through the narrow slot 426 ofthe output hinge and the other ends of the plate protruding out throughthe wide slot 428. A spring 426 stretches between the middle of the twoplates 434 pushing the plates apart so that there is an angle betweenthe plates and neither plate lies along the diameter of the outputhinge.

FIG. B17 shows an exploded view of the main components of the fixedassembly 406 which includes a hollow metal fixed cylinder 438 which fitswithin a housing block 440 and is secured to the housing block by a setscrew 442. Housing block 440 is basically shaped like a metal block witha large hole 444 that runs horizontally through the block and withinwhich fixed cylinder 438, which is the outermost cylinder of the threenested cylinders in the anti-backdrive mechanism, is seated. Set screw442 passes through a small hole 446 which runs vertically down from thetop of the housing block and empties into the large hole 444 where itmakes firm contact with the outer surface of the fixed cylinder 438 tokeep the fixed cylinder from moving within the housing block. Along thetop and the bottom of the housing block there is a narrow rectangularstrip with two holes along the top strip and two holes along the bottomstrip, through which pass bolts 450 with lock washers to rigidly mountthe housing block to the internal saw structure.

The anti-backdrive mechanism is assembled with the input hinge 408overlapping the output hinge 420, as shown in FIG. B18. The nestedhinges are oriented so that the narrow slot 426 in the output hinge 420overlaps one of the wide slots 414 in the input hinge 408, as can beseen in FIG. B19. The edges of the plates 434 extend out slightlythrough narrow slot 426 and the overlapping wide slot 414, as can beseen in FIG. B20. The other edges of plates 434 extend out through thewide slot 428 in the output hinge 420 and through the other wide slot414 in the input hinge 408 which overlaps wide slot 428. The narrow slot426 in the output hinge holds the ends of the two plates close togetherwhile the compressed spring 436 stretching between the middle of the twoplates 434 pushes the plates apart so that the ends of the platesopposite the narrow slot 426 are spread apart until each plate hits theside of the wide slot 414 in the input hinge nearest each plate. Theplates 434 are thus oriented with an angle between them with thedistance between the ends of the plates that protrude through the wideslots 414 in the input hinge 408 set by the width of the wide slot 414in the input hinge 408.

As shown in FIG. 321, the input and output shaft assemblies arepositioned within the fixed cylinder 438 of the fixed assembly 406 whichhas no slots. Plates 434 are sized so that the height of each plate isless than the diameter of the fixed cylinder but will only fit withinthe fixed cylinder if the plates are aligned along the diameter of thecylinder. When the spring is allowed to push the plates apart so thatthey lie against the sides of the wide slot 414 in the input hinge theplates would not lie along the diameter and would thus protrude past theouter surface of the output hinge and would not fit within the fixedcylinder. Thus plates 434 are pushed together and spring 436 compressedenough to allow the plates to fit within the fixed cylinder. Oncepositioned inside the fixed cylinder the spring is released and pushesthe plates apart so that the plates make contact with the inner surfaceof the fixed cylinder. While in this configuration, which is the defaultconfiguration, the edges of the plates 434 are wedged by the spring 436against the inner surface of the fixed cylinder 438 which has no slotsand prevents the input and output assemblies from rotating. FIG. B22shows a diagram that illustrates a plate extending past the output hingewhen it does not lie along the diameter of the output hinge.

Since the wide slot 428 in the output hinge 420 is wider than the wideslot 414 in the input hinge 408 which it overlaps, the sides of the wideslot 428 in the output hinge are not in contact with the plates in thedefault configuration but the sides of the narrow slot 426 in the outputhinge are in contact with the plates. Consequently, an attempt to rotatethe output hinge amounts to a force applied to the plates by the side ofthe narrow slot 426 in the output hinge that results in further wedgingthe edge of one of the plates extending out through wide slot 428 in theoutput hinge against the inner surface of the fixed cylinder 438. Whenan attempt is made to rotate the output hinge in the opposite direction,the other plate wedges against the fixed cylinder. Thus, theanti-backdrive mechanism locks due to a wedged plate when an attempt ismade to rotate the output shaft 422 in either direction so that neitherthe output shaft 422 nor the input shaft 410 may rotate.

When an attempt is made to rotate the input shaft 410, which is rigidlyattached to the input hinge 408, a different situation arises. In thedefault configuration, the plates are kept apart at an angle by thespring 436 placed between them, but compressing the spring reduces theangle between the plates enough to set the plates free so they mayrotate. Since the wide slot 414 in the input hinge is more narrow thanthe wide slot 428 in the output hinge, one side of slot 414 in the inputhinge overlapping slot 428 will push against the nearest plate when theinput hinge rotates which will tend to move that end of the platetowards the other plate by compressing spring 436 so that the plate ismore closely aligned with the diameter through the input and outputhinges and the fixed cylinder. Since the wide slots 414 in the inputhinge are much wider than the narrow slot 426 in the output hinge, noforce is applied at this point to the plates near the narrow slot by theinput hinge and the edges of the plates through the narrow slot willremain wedged against the fixed cylinder until the angle between theplates decreases enough to unwedge the plate 434. Once one plate isunwedged then the edge of the wide slot 414 in the input hingeoverlapping narrow slot 426 will contact one of the plates and bothplates along with both input and output hinges will rotate as the inputhinge rotates. Bringing the plates into alignment with the diameter ofthe fixed cylinder frees the plates so that they may rotate with theinput and output hinges since they are shorter than the diameter of thefixed cylinder and neither the top or bottom edges of the plates wouldbe wedged against the inner surface or the fixed cylinder. Thus turningthe input shaft which is rigidly attached to the input hinge will unlockthe anti-backdrive mechanism by unwedging a plate allowing the rotationto be communicated to the output shaft so that both the input shaft andthe output shaft rotate.

FIGS. P1 through P23 d show an anti-backdrive mechanism 500 built arounda set of four metal plates linked to a hollow cylinder which is fixed tothe saw structure and thus unable to move with respect to the othercomponents of the anti-backdrive mechanism. Once again the overallassembly is composed of three main sub-assemblies: an input shaftassembly 502 shown in FIG. P1, an output shaft assembly 504 shown inFIG. P2 and a fixed assembly 506 shown in FIG. P3. The complete assemblyincorporating anti-backdrive mechanism 500 is shown in FIG. P4.

FIG. P5 shows an exploded view of the input assembly 502 which consistsof a cylindrical input hinge 508 attached to an input shaft 510 by aspring pin 512. Input hinge 508, shown isolated in FIGS. P6 through P9,is shaped like a hollow cylinder with portions removed longitudinallyalong the cylindrical shell so as to leave four walls of the same lengthalong the perimeter with gaps 514 in between. Two of the walls 518 areof a shorter arc length than the other two walls 520, as shown best inFIG. P9, but the four gaps 514 are the same size and are spaced so thatwalls that are across from each other are of the same size. The wallsare joined to a short, solid cylinder that has a large circular recessedarea 516 in the center of the outward facing end opposite the end wherethe walls are attached. The input shaft is shaped like a cylindrical rodwith flat surface cut longitudinally in one end to mount a handwheel.The other end of the input shaft has a short cylindrical section 511 oflarger diameter. The larger diameter section 511 of the input shaft 510fits within the large circular recessed area 516 at the end of the inputhinge. The input hinge 508 is mounted to the input shaft by a spring pin512 which passes through a small hole 524 in the side of the input hingethat exits along the side of the large circular recessed area 516, thenthrough a hole 526 that goes through the input shaft and finally throughanother small hole 524 in the side of the input hinge.

FIG. P10 shows an exploded view of the output assembly 504 whichconsists of a cylindrical output hinge 528 attached to an output shaft530 by a spring pin 532. As shown in FIGS. P11 through P14, output hinge528 is shaped like a cylinder which is mostly solid except for a largehole 534 running through the center along the length of the cylinder anda pattern carved deeply, about one-third the length of the cylinder,into one end. The pattern is shown best in FIG. P14 which looks directlyat the patterned end of the output hinge. In forming the pattern, firstan ‘X’ is carved across and centered within the end of the cylinder. Inthe top and bottom quarters marked off by the ‘X’ a wall 536 of shortlength runs along each side of the ‘X’ from the hole 534 in the centerof the cylinder to a little over one-third the distance from the hole inthe center of the cylinder to the outer surface of the cylinder. Thecylinder is cut away from the end of the wall 536 to the outer surfaceof the cylinder sweeping through an angle of about sixty degrees withthe side of the ‘X’ forming a wall 538 and carving out a generallytriangular area 540 out towards the outer surface of the cylinder. Thusa solid projection 541 is formed the perimeter of which is defined by awall 538 joined to a wall 536 joined to a portion of the contour of hole534 in the center of the cylinder which is joined to another wall 536joined to another wall 538 which joins the counter of the outsidesurface of the hinge. In each of the side quarters marked off by the ‘X’a wall 542 runs alongside the ‘X’ from the outer surface of the cylinderinward for a length equal to about a little less than one-fourth thedistance from the hole in the center of the cylinder to the outersurface of the cylinder. The cylinder is cut away beginning at the endof each wall 542 and moving toward the center of the cylinder sweepingthrough an angle of about thirty degrees with the each side of the ‘X’respectively forming a wall 544 carving out an area 546 along each sideof the ‘X’. Thus a solid projection 547 is formed the perimeter of whichis defined by a wall 542 joined to a wall 544 joined to another wall 546joined to another wall 542 which joins the counter of the outsidesurface of the hinge. Two small holes 548 coaxially aligned with eachother, one located above the large center hole 534 and one below, passthrough the end of output hinge opposite the patterned end. The outputshaft 530 is attached to the output hinge 528 by a spring pin 532 whichpasses through the small holes 548 in the output hinge and a hole 550 inthrough output shaft.

As shown in FIGS. P3 and P15, a hollow fixed cylinder 552 is held inposition by a collar 554, made up of two semicircular half-pieces 556and 558, that fits around the fixed cylinder and has a vertical flatsurface 560 along the side with two threaded holes 562 in it for twoscrews that rigidly mount the collar 554 to the saw structure. As shownin FIG. P15, there is a hole 564 running horizontally through each endof the vertically oriented half-collar piece 556 through which passscrews 566, one screw at each end of the half-collar piece, which threadinto threaded holes 568 that run horizontally through each end of thecorresponding vertically oriented half-collar piece 558 to hold the twosemicircular half-pieces of the collar together. The socket head capscrews allow the collar to be clamped tightly around the fixed cylinderholding it firmly in place so that it cannot move relative to the othercomponents of the anti-backdrive mechanism. Four plates 570 are setaround the fixed cylinder 552, as shown in FIG. P3. Each plate 570,shown isolated in Figures P16 and P17, is shaped like a flat squaremetal plate with a U 572 shaped cutout that cuts into the plate fromalong one side continues for about two-thirds the length of the platecurves back around and exists the side it entered. The U is centeredalong the side of the plate and the edges are rounded all along the cutso that when looking at the side of the plate that the cut enters, itlooks like a long rectangular area extending down from one edge of theplate which is capped with a semicircular area and followed by an openarea to the midpoint of the side of the plate beyond which there is moreopen area then another semicircular area oriented so that the straightside of the semicircle joins another long rectangular area thatstretches to the other end of the plate so that the bottom half mirrorsthe top half. The U cutouts with their rounded edges allow the fourplates to slip over the edge of the hollow fixed cylinder 570 and rotateslightly from side to side. When the plates are oriented so that theyare perpendicular to the outer surface of the fixed cylinder, orapproach perpendicular, they are free to move along the cylinderunhindered but when they are slanted at an angle of roughly sixtydegrees or less to the outer surface of the fixed cylinder 570 theybecome jammed or wedged against the fixed cylinder and are not able tomove. Rotating the plates even a few degrees from their wedged, orlocked position, frees the plates so that they are able to slide alongthe side of the fixed cylinder.

FIG. P18 shows fixed assembly 506 installed on the output assembly 504with the output hinge 528 seated within the fixed cylinder 552. Thewidth of each line forming the ‘X’ pattern in the output hinge is equalto the width of a plate 570 and the four plates 570 fit in the carved‘X’ pattern, with one plate 570 in each leg of the ‘X’ pattern, whichpartially determines the orientation of the plates to the fixedcylinder. Walls 536, 538, 542, and 544 in the output hinge orient eachplate perpendicularly to the cylinder and areas 540 and 546 carved outof each quarter of the ‘X’ pattern provide room for the plates 570 torotate, so that the two plates in the upper quarter of the ‘X’ patterncan rotate towards each other and the two plates in the lower quarter ofthe ‘X’ pattern can rotate towards each other to lock the plates againstthe cylinder. As shown in FIGS. P18 and P19, a spring 574 stretchesbetween the two plates 570 in the upper quarter of the ‘X’ at the outerends of the plates and another spring 574 stretches between the twoplates 570 in the bottom quarter of the ‘X’ at the outer ends of theplates to keep the plates rotated so that they are wedged, or locked,against the fixed cylinder and lie against walls 544 of the output hingewhich is the default state of the anti-backdrive mechanism. The inputhinge is axially aligned with the output hinge and placed over the endof the fixed cylinder with each plate 570 passing though one of the gaps514 in the input hinge. The walls 518 of shorter arc length on the inputhinge are positioned between each pair of plates that share a spring574, as shown in FIG. P19.

FIGS. P20 through P23 d show the relative positions of the input hinge508, the output hinge 528 and plates 570. FIG. P20 shows the relativepositions of the input hinge, output hinge and plates when theanti-backdrive mechanism is in the default state looking down the outputshaft towards the anti-backdrive mechanism. FIG. P21 shows the same viewbut with the output hinge transparent so both the walls of the inputhinge and the ‘X’ pattern on the output hinge can be seen. In thedefault state the four plates are wedged against the fixed cylinder 552so that neither the output shaft nor the input shaft can rotate when atorque is applied to the output shaft. When an attempt is made to turnthe output shaft, and thus the output hinge attached to the outputshaft, two of the plates 570 tend to rotate in a direction that makesthem less perpendicular to the surface of the cylinder and those platesbecome more strongly wedged against the fixed cylinder preventing theoutput shaft from turning. As shown in FIG. P22 in which the outputhinge is transparent, attempting to rotate the output shaft clockwisecauses the upper right and lower left plates 570 to wedge against thefixed cylinder 552. Attempting to rotate the output shaft in the otherdirection causes the other two plates 570 to wedge against the fixedcylinder 552. Thus, in the default state of the anti-backdrive mechanismthe output shaft is not able to rotate when a torque is applied to theoutput shaft.

The input hinge 508 attached to the input shaft 510 is used to releaseor unlock the anti-backdrive mechanism. FIGS. P23 a through P23 d, whichshow the relative positions of the input hinge, output hinge, andplates, with the output hinge transparent, illustrate the process bywhich the anti-backdrive mechanism is released. When a torque is appliedto the input shaft, input hinge 508 rotates, as shown in FIG. P23 a,stretching the two springs 574, as shown in FIG. P23 b, and a corner ofeach wall 518 of shorter arc-length on the input hinge hits the nearestplate 570 and the two plates rotate in the direction that the inputshaft is turning making the plates parallel to the surface of the fixedcylinder so that they are free to move along the cylinder, as shown inFIGS. P23 a and P23 b. As the input hinge further rotates, the two freeplates push against their corresponding walls 542 on the output hinge,as shown in FIG. P23 b, and this causes the output hinge to startrotating, as shown in FIG. P23 c. As the output hinge rotates, it pushesagainst the sides of the other two plates that have not yet rotatedwhich provide no resistance due to their orientation and they rotateenough in the opposite direction the that input shaft is turning thatthey unwedge from the fixed cylinder and are dragged along as the inputand output hinges rotate, as shown in FIGS. P23 c and P23 d. Thus theanti-backdrive mechanism is released or unlocked when the input hingerotates so that both the input shaft and output shaft rotate.

FIGS. C1 through CX show another example of an anti-backdrive mechanism.This anti-backdrive mechanism 600 uses the orientation of two platesrelative to a fixed structure to lock or unlock the mechanism. Onceagain the overall assembly is composed of three main sub-assemblies: aninput shaft assembly 602 shown in FIG. C1, an output shaft assembly 604shown in FIG. C2 and a fixed assembly 606 shown in FIG. C3. The completeassembly incorporating anti-backdrive mechanism 600 is shown in FIG. C4.

Input assembly 602, shown in the exploded view of FIG. C5, is composedof an input shaft 608 attached to two input shaft plates 610 by fourflat head screws 612. Input shaft 608 is shaped like a rod with a flatsurface 614 cut about one-sixth the diameter of the shaft deep into theshaft at one end along the top of the shaft upon which the handwheel ismounted. At the other end of the shaft there are two rectangular flatsurfaces 616 cut longitudinally about one fourth the diameter of theshaft deep into the shaft on opposite sides of the input shaft so thatthe flat surfaces 616 run parallel to each other and perpendicular tosurface 614. The flat surfaces extend along the input shaft for about alittle less than an inch, which is a little less than about one thirdthe length of the input shaft. Each flat surface 616 has two threadedholes 618 situated along the midline running through the length of eachflat surface, one hole located towards each end of the flat surface. Aninput shaft plate 610 fits up against each flat surface 616 at the endof the input shaft 608 as shown in FIGS. C5 and C6. Each input shaftplate 610 is shaped like a rectangular plate with the long sides onlyslightly longer than the short sides, as shown in FIGS. C7 through C9which shows an isolated view of the right input shaft plate. The leftinput shaft plate is a mirror image of the right input shaft plate.Plates 610 fit up against the input shaft with the long sides of theplates perpendicular to the shaft. The short sides of the plates extendbeyond the end of the shaft by about half an inch. The outermostsurfaces of the plates are slightly recessed along a rectangular area620 that runs along the edge of the long side of the plate beyond theshaft, as shown in FIG. C6. Two ‘U’ cutouts 622 are cut into each platefrom along the outermost long side extending beyond the end of the shaftso that each ‘U’ lies parallel to the input shaft with one ‘U’ above theinput shaft and the other ‘U’ below the input shaft. There is a taperededge 624 along each ‘U’ which is tapered such that more of the plate iscut away moving from the surface of the plate that abuts the input shaftto the outer surface. The edge of the ‘U’ cutout 622 that lies along thesurface of the plate which sits up against the shaft extends into theplate as far as the recessed area 620 extends on the outermost surfaceof the plate and the ‘U’ along the outermost surface extends just beyondthe edge of the recessed area 620. Both the recessed areas 620 and the‘U’ cutouts 622 end just before reaching the end of the input shaft. Twoholes 626 are drilled into each plate in the non-recessed area of eachplate along the midline running through the plate from one long side tothe other long side. Holes 626 are cut with countersunk areas 628 underthe heads of the screws to accommodate flat head screws 612 so that thehead of each screw lies flush with the outer surface of the plate. Theflat head screws 612 pass through holes 626 in the input shaft platesand thread into corresponding threaded holes 618 located in the flatsurfaces 616 input shaft.

Output assembly 604, shown in the exploded view of FIG. C10, includes anoutput shaft 630 attached to an output shaft plate 632 through whichextends a spring 634. Output shaft 630, shown isolated in FIGS. C11through C13, is shaped like a rod with two generally rectangularprojections 636 sticking out longitudinally from one end which areparallel to each other with a gap 638 between them, as seen best inFIGS. C11 and C13. The rectangular projections are formed as of from acylinder of smaller diameter than the diameter of the output shaftpositioned concentrically with the output shaft with a strip cut out inthe middle so that there are left two generally rectangular projections636 with gap 638 between them. On the outermost sides of eachrectangular projection there is a longitudinally oriented flatrectangular area 640 which extends inward from the end of the outputshaft about three-fourths the length of the rectangular projections andwhich is vertically centered on the rectangular projections, as can beseen best in FIG. C12. There are three holes 642, 644 and 646 in eachrectangular projection 636 and the holes in one rectangular projectionare aligned with the holes in the other rectangular projection, forexample, hole 642 in one rectangular projection is directly across fromhole 642 in the other rectangular projection. Holes 644 and 646 arewithin the region of the flat rectangular surface 640, with hole 646located towards that end of the output shaft, and hole 642 is betweenthe end of the cylindrical section of the output shaft and the flatrectangular surface 640. All three holes are aligned along the midlinerunning parallel to the rectangular projections and hole 646 is slightlylarger than holes 642 and 644, as can be seen in FIG. C12. Output shaftplate 632, shown isolated in FIGS. C14, is shaped like a largerrectangle 648 with a smaller rectangular extension 650 that liesparallel to the larger rectangle and extends out from the middle of oneof the long sides of the larger rectangle. The extension 650 is about aslong as the larger rectangle is wide and the short side of the smallerrectangle abuts the long side of the larger rectangle so as to form ashort, stubby ITT shape oriented sideways. There is a hole 652 in thelarger rectangular piece of output shaft plate 632 that is centeredbetween the two short sides of the rectangle but is closer to the longside with the extension than to the other long side. In the smallerrectangular extension 650 there are two smaller holes 654 and 656situated side-by-side whose centers are aligned along the same line thatpasses through the center of the larger hole 652 in the larger rectangle648. A narrow collar 658 shaped like a narrow slice of a hollow cylindercut along two sides two form two flat surfaces 659 that are positionedparallel to and across from each other fits over the rectangularprojections and is seated between the cylindrical portion of the outputshaft and the flat rectangular surface 640. Collar 658 has two holes 660that pass through the flat surfaces 659 on each side of the collar tothe large hole 662 through the center of the collar. Output shaft plate632 is situated between the parallel extensions 636 of the output shaft630 and a pin 664 passes through holes 660 on the collar, through holes642 in each rectangular projection 636 and through hole 654 in theoutput shaft plate to help secure the output shaft plate to the outputshaft. Output shaft plate 632 is also mounted to the end of the outputshaft 630 by a screw 668 that passes through holes 644 in therectangular projections 636 and through the hole 656 in the output shaftplate 632. Spring 634, shaped like a straight coil about an inch inchlong passes through holes 646 in the rectangular projections and hole652 in the output shaft plate and is centered about the output shaftplate extending out to either side about three-eighths of an inch, ascan be seen in FIG. C2.

FIG. C16 shows an exploded view of the fixed assembly 606. The fixedassembly 606 includes a fixed brake plate 670, shown isolated in FIG.C17, which is shaped like a metal plate vertically oriented with a largecircular cutout 672 centered vertically and positioned horizontally moretoward one side, and which has two holes 674, lined one above the other,along the opposite side. A screw passes through each hole 674 to rigidlyattach the brake plate to the internal saw structure so that the brakeplate is unmovable with respect to the other components in theanti-backdrive mechanism. The ends of two rectangular rotating plates676, oriented so that they mirror each other, fit through the largecircular cutout 672 in the brake plate 670 with the rotating plates andare positioned so that flat surfaces 677 on the edges along the lengthof each plate are coplanar and the faces of the plates facing each otherare either nearly parallel or have a slight angle between them as theplates pivot mildly about a line running perpendicular to the longsides. FIGS. C18 and C19 show a rotating plate 676 isolated. Eachrotating plate 676 is generally a rectangular plate with two holes 678and 680 drilled into the surface 677 of the long, thin side edge of theplate so that they run parallel to the plate. Hole 678 is located nearthe end of the plate and closer to one face of the plate and the otherhole 680 is located more towards the center of the plate and closer tothe other face of the plate. On one edge 681 along the short side of therotating plate, the edge nearest to holes 678 and facing the otherrotating plate, is rounded, as shown in FIG. C18. The same pattern isrepeated on the opposite side edge of the plate so that the two holes678 near the end of the plate are axially aligned and the two holes 680towards the center of the plate are axially aligned. A metal dowel pin682 is inserted into each of the four holes 678 and 680 and extendsoutward from the edges of the plate about one-quarter inch. Each pair ofpins 682 on the same plate side edge straddles the brake plate with theholes 678 and 680 towards the end of each plate on the back side of thebrake plate and the pins nearest the face of each plate which faces theother plate on the front side of the brake plate. Along the shorter sideof each rotating plate 676 opposite the end near the brake plate thereare two threaded holes 684, one near each corner of the plate. A customscrew 686 which has a button styled head without a socket and a threadedportion with a hexagonal socket in the end is inserted into each hole684 from the inner face of the plate to the outer face so that thebutton heads are faced inward and toward the button heads of the screwson the other plate. The hexagonal sockets allow for adjusting thescrews.

The anti-backdrive mechanism is assembled with the output shaft plate632 seated in the gap between the heads of the custom screws 686 on therotating plates 676 in the fixed assembly and the output shaft passingbetween the rotating plates 676 and through the large circular cutout672 in the brake plate 670 of the fixed assembly, as shown in FIG. C4.The rounded sides of collar 658 serve as a standoff between the rotatingplates around the point where the plates pivot. The input shaft iscoaxially aligned with the output shaft and the ‘U’ cutouts 622 on theinput shaft plates fit about the custom screws 686 on the rotatingplates in the fixed assembly. Rounded edges 681 along the short sides ofeach rotating plate which face each other and are nearest to holes 678allow the rotating plates to be at an angle to the brake plate withoutinterference with the output shaft.

When the rotating plates 676 are parallel to each other, and thusperpendicular to the brake plate 670, the distance between each pin 682in a pair sharing the same surface 677 is greater than the thickness ofthe brake plate and the plates are free to move along the edge of thelarge circular cutout 672 in the brake plate so that they can rotatearound in a circle. But as the ends of the rotating plates 676 farthestaway from the brake plate are spread apart they reach an angle of aboutfive degrees (confirm with Jamie) between the rotating plates 676 atwhich the plates are stopped from spreading farther apart by pins 682because the distance between each pin in a pair has come to equal thethickness of the brake plate thus preventing further rotation of therotating plate. Attempting to spread the plates farther apart causes thepins 682 to jam against the brake plate 670 so that the plates do notmove relative to the brake plate. When the plates are jammed against thebrake plate, the anti-backdrive mechanism is locked. A spring 634stretches between the inner face of each plate near the end farthestfrom the brake plate to push the plates apart so that the default stateof the anti-backdrive mechanism is the locked state. Attempting torotate the output shaft when the anti-backdrive mechanism is in thelocked state causes the output shaft plate to push against the heads oftwo of the custom screws 686 in the rotating plates which tends to pushthe rotating plates farther apart further jamming the pins 682 againstthe brake plate 670, as illustrated in FIGS. C20 and C21. Rotating theoutput shaft in the opposite direction causes the output shaft plate topush against the heads of the other two custom screws 686 again jammingthe anti-backdrive mechanism so that the input and output shafts willnot rotate.

FIGS. C22 and C23 illustrate what happens when the input shaft isrotated. When the input shaft is turned, the input shaft plates rotateand hit against the underside of the button-head custom screws 686 whichpulls two of the screws, one above the input shaft and one below,inward. That, in turn, pulls the ends of the rotating plates inwardmaking the rotating plates more parallel. This frees the rotating platesso that they can rotate along with the input shaft and the heads of thebutton head screws push on the output shaft plate so that it rotates aswell. Rotating the input shaft in the opposite direction pulls the othertwo screws, one above the input shaft and one below, which again drawsthe rotating plates inward so they are more parallel and free to rotate.Turning or rotating the input shaft thereby releases the anti-backdrivemechanism. The custom screws 686 allow for adjusting the amount of playthere is when the input shaft is rotated before it engages the platesand turns the output shaft. Tightening the four screws 686 moves theends of the rotating plates 676 closer together so that the plates arecloser to being parallel to each other in the default state which meansthat the input shaft does not need to rotate as much to release theanti-backdrive mechanism.

FIGS. A1 through AX show an anti-backdrive mechanism 700 that uses theorientation of a movable plate assembly relative to a fixed platerigidly attached to the saw structure to lock or unlock theanti-backdrive mechanism. Once again the overall assembly is composed ofthree main sub-assemblies: an input shaft assembly 702 shown in FIG. A1,an output shaft assembly 704 shown in FIG. A2 and a fixed assembly 706shown in FIG. A3. The complete assembly incorporating the anti-backdrivemechanism 700 is shown in FIG. A4.

Input assembly 702, shown in the exploded view of FIG. A5, is composedof an input shaft 708 attached to an input cylinder 710. Input shaft 708is shaped like a cylindrical rod with a flat surface 712 cutlongitudinally for about an inch along one end of the input shaft formounting a handwheel. At the other end of input shaft 708, there is alarger diameter section 714 which is about one-sixth the length of theinput shaft and has a diameter about twice that of the rest of theshaft. There is a hole 716 running through the larger diameter section714 from one side to the other which is centered along the length of thelarger diameter section 714. Input cylinder 710, shown isolated in FIGS.A6 through A8, is shaped like a hollow cylinder sized to fit over thelarger diameter section 714 of the input shaft and which has two wideslots 718 with rounded corners cut longitudinally into the cylinder andaligned directly across from each other leaving two equally sizedextensions 720 along the perimeter of the cylinder. Slots 718 are aboutas wide as a little over one-fourth the perimeter of the cylinder andare cut into the cylinder starting from one end and continuing for alittle over two-thirds the length of the cylinder. In the last one-thirdof the length of the cylinder where slots 718 do not extend, there aretwo small holes 722 aligned across from each other and positioned alonglongitudinal midlines running through slots 718. A spring pin 724 passesthrough holes 722 in the input cylinder and through hole 716 in theinputs shaft to attach the input cylinder 710 to the input shaft 708.

Output assembly 704, shown in the exploded view of FIG. A9, is composedof an output shaft 726 attached to an output cylinder 728. Output shaft726 is shaped like a cylindrical rod with a larger diameter section 730at one end which has a diameter about twice the size of the diameter ofthe rest of the output shaft and which is about one-sixth the length ofthe output shaft. There is a hole 732 running through the largerdiameter section 730 from one side to the other which is centered alongthe length of the larger diameter section 730. Output cylinder 728,shown isolated in FIGS. A10 through A13, is shaped like a hollowcylinder sized to fit over the larger diameter section 730 of the outputshaft and which has two angled slots 734 that start at one end andcontinue inward and at an angle of about thirty degrees from horizontaltowards the opposite side of the cylinder for about two-thirds thelength of the cylinder. Each slot 734 covers an arc-length of aboutone-eighth the perimeter of the cylinder, as can be seen best in FIG.A11. Between slots 734 there are extensions which are remnants leftalong the perimeter of the cylinder, one extension 736 which has asmaller arc-length at the end of the cylinder where the slots begin, alittle over one-eighth the perimeter of the cylinder, and one extension738 which has a larger arc-length at the end of the cylinder where theslots begin, a little over one-half the perimeter of the cylinder, ascan best be seen in FIG. A11. In the last one-third of the length of thecylinder where slots 734 do not extend, there are two small holes 740aligned across from each other and positioned along a line runninghorizontally through the cylinder and which is midway between parallellines running through each end of slots 734. A spring pin 742 passesthrough holes 740 in the output cylinder and through hole 732 in theoutput shaft to attach the output cylinder 728 to the output shaft 726.

Fixed assembly 706, shown in the exploded view of FIG. A14, is composedof a fixed brake plate 744 and a movable plate assembly 746. Brake plate744 is shaped like a generally square metal plate, vertically oriented,with a large circular cutout 748 centered vertically but shifted more toone side horizontally. Along the other side there is a rectangular block750 which is vertically oriented and has two holes 752, one toward thetop and one toward the bottom of the rectangular block for screws 754 topass through to rigidly mount the fixed brake plate to the internalstructure of the saw. The rectangular block may be a separate pieceattached to the brake plate with screws that pass through holes 755, onenear the top of the block and one near the bottom, and throughcorresponding holes in the brake plate. FIGS. A15 through A17 showmovable plate assembly 746 which consists of two rectangular slabs 756held together by an ‘H’ shaped block 758 that is almost as deep as theslabs are long and which is inserted between the slabs to hold the edgesof the two slabs together with the open ends 760 of the ‘H’ sized to fitthe thickness of the rectangular slabs. The rectangular slabs 756 aremirror images of each other and the rectangular slab 756 that appears tothe left in FIG. A14 which views the fixed assembly from the side of theinput shaft, is shown isolated in FIGS. A18 through A20. Along themiddle of the long side of each rectangular slab 756 opposite the sideinserted into the shaped block there is a notch 762 cut out of the slabthat looks like a square cut all the way through the rectangular slabwhen looking down at the face of the rectangular slab, as shown in FIG.A20. When looking along the outside edge of the rectangular slab alongwhich the notch is cut out, however, notch 762 looks more like an ‘X’ inthat the sides of the notch are cut at angles. As can be best seen inFIG. 19 which shows a side view of the rectangular slab 756 facing notch762, the angled cut along the side of notch 762 that appears to the leftin FIG. 19 consists of a short segment 764 of negative slope which joinsa longer segment 766 of positive slope. The short segment of a negativeslope starts from the top face of the slab at a point between the edgeof the long side that appears to the left on the rectangular slab inFIG. 19 and the middle of the long side of the rectangular slab butcloser to the middle, and stops before reaching the midline runninglongitudinally through the long side of the rectangular slab. The longersegment 766 starts where the short segment stops and continues towardsthe bottom face of the rectangular slab along a positive slope. Theangled cut along the side of notch 762 that appears to the right in FIG.19 is also made up of two segments, a longer segment 766 with a negativeslope and a shorter segment 764 with positive slope. The longer segment766 starts from the top face of the rectangular slab at a point betweenthe edge of the long side that appears to the right on the rectangularslab in FIG. 19 and the middle of the long side of the rectangular slabbut closer to the middle, and stops just beyond the midline runninglongitudinally through the long side of the rectangular slab at whichpoint it joins a shorter segment 764 of negative slope that continuestoward and stops at the bottom face of the rectangular slab. The pointsat which the longer and shorter segments 764 and 766 of each angled cutmeet forms peaks 768 and 770 which are rounded and slightly set off fromeach other as the upper and lower sloped segments on each side are of aslightly different length with the peak 768 that appears along the leftside of the notch in FIG. 19 positioned a little above the longitudinalmidline of the long side of the rectangular plate and peak 770 thatappears along the right side of the notch in FIG. 19 positioned a littlebelow the longitudinal midline of the side.

The anti-backdrive mechanism is assembled as shown in FIG. A4. Outputcylinder 728 has an inner diameter that is slightly larger than theouter diameter of the input cylinder 710 and fits over the inputcylinder with the slotted end of the input cylinder inserted into theslotted end of the output cylinder and the input shaft 708 coaxiallyaligned with the output shaft 726. The input and output cylinders 710and 728 are rotated with respect to each other so that the angled slots734 in the output cylinder overlap the wide slots 718 in the inputcylinder. The input and output cylinders are positioned within the largecircular cutout 748 in the fixed plate, as shown in FIG. A4, and themovable plate assembly 746 is positioned within the input and outputcylinders, 710 and 728, with the rectangular slabs 756 extending out toeach side through slots 718 and 734 in the input and output cylinders,and the notches 762 on each side of the rectangular slabs fitted aroundthe edge of the large circular cutout 748. As shown in FIG. A23, thepeaks 768 and 770 along the sides of each notch 762 in the rectangularslabs 756 of the movable plate assembly make contact with the fixedbrake plate 744. The movable plate assembly is positioned within theinput and output cylinders in such a way that when the output cylinderis oriented so that the angled slots 734 in the output cylinder slopedownward moving from the open end of the output cylinder toward the endattached to the output shaft, the short segments 764 of the angled cutsalong the side of notches 762 of the rectangular slabs are above thelonger segments 766 on the side of the brake plate facing the outputshaft so that peaks 768 ride along the rear surface of the brake plate.The distance between peaks 768 and 770 is a little larger than thethickness of the brake plate 744 so that the movable plate assembly 746would rest freely at an angle relative to the brake plate in the absenceof the input or output cylinders. Slots 734 in the output cylinder areangled in such a way that they slope in the same direction as therectangular slabs 756 in the movable plate assembly would slope ifhanging freely against the brake plate, as shown in FIG. A23, though theslope of the angled slots is more steep than the slope of the movableplate. The width of each slot 734 in the output cylinder 728 is suchthat when the output cylinder is oriented so that slots 734 slopedownward moving from the front of the anti-backdrive mechanism towardthe rear, as shown in FIG. A24, the front, outside corner of one of therectangular slabs 756 contacts the bottom of one of the slots 734 andthe rear, outside corner of the other rectangular slab 756 contacts topof the other slot 734. When the output cylinder is rotated around sothat it is oriented so that the slots 734 slope upward moving from thefront of the anti-backdrive mechanism toward the rear, then the front,outside corner of one of the rectangular slabs 756 contacts the top ofone of the slots 734 and the rear, outside corner of the otherrectangular slab 756 contacts bottom of the other slot 734. The angleand width of slots 734 allow the rectangular slabs to remain lodgedagainst the fixed brake plate 744. The width of the wide slots 718 inthe input cylinder 710 are sized so that they do not contact therectangular slabs 756 unless the input cylinder is rotated about 10degrees at which point the top of one slot would contact the front,outside corner of one of the rectangular slabs and the bottom of theother slot would contact the rear, outside corner of the otherrectangular slab, if the output cylinder is oriented such that slots 734slope downward moving from the front of the anti-backdrive mechanismtoward the rear as shown in FIG. A25.

In the default state of the anti-backdrive mechanism when no torques areapplied to either the input or output cylinders the movable plateassembly 746 assumes a default orientation in which the rectangularslabs 756 of the movable plate assembly are lodged, or wedged againstthe fixed brake plate 744 so that the input and output assemblies areunable to rotate and the anti-backdrive mechanism is locked. When thereis an attempt to rotate the output shaft, as shown in FIG. A24, theslots 734 in the output cylinder push against the rectangular slabs 756of the movable plate assembly at the front, outside corner of onerectangular slab and the rear, outside corner of the other rectangularslab kitty-corner from the first corner which tends to rotate themovable plate assembly 746 in such a way as to increase the angle of themovable plate assembly to the fixed brake plate 744 more firmly wedgingrectangular slabs 756 against the fixed brake plate 744. An attempt torotate the output shaft in the other direction causes the slots 734 inthe output cylinder to contact the other front and rear corners of therectangular slabs 756 which also tends to rotate the movable plateassembly 746 in such a way as to increase the angle of the movable plateassembly to the fixed brake plate 744 more firmly wedging therectangular slabs 756 of the movable plate assembly 746 against thebrake plate 744. Thus an attempt to rotate the output shaft in eitherdirection, clockwise or counter-clockwise causes the movable plateassembly to further jam against the fixed brake plate preventing theinput and output shafts from rotating and locking the anti-backdrivemechanism.

A different situation arises when the input shaft is rotated. When theinput shaft rotates, as shown in FIG. A25, the wide slots 718 in theinput cylinder 710 contact the rectangular slabs 756 of the movableplate assembly at the front, outside corner of one rectangular slab andthe rear, outside corner of the other rectangular slab kitty-corner fromthe first corner which tends to rotate the movable plate assembly 746 insuch a way as to decrease the angle of the movable plate assembly to thefixed brake plate 744 thereby freeing the movable plate assembly so thatit may rotate along with the input cylinder. As the movable plateassembly rotates, the rectangular slabs 756 push on the output cylinderso that both the input and output assemblies rotate with the rotatinginput shaft. An attempt to rotate the input shaft in the other directioncauses the slots 718 in the input cylinder to contact the other frontand rear corners of the rectangular slabs 756 which also tends to rotatethe movable plate assembly 746 in such a way as to decrease the angle ofthe movable plate assembly to the fixed brake plate 744 thus freeing themovable plate assembly and enabling the input and output assemblies torotate along with the rotating input shaft. Thus an attempt to rotatethe input shaft in either direction, clockwise or counter-clockwisecauses the movable plate assembly to rotate freely, bound by but notwedged against the edge of the large circular cutout 748 of the fixedbrake plate, thus allowing the input and output shafts to rotate andunlocking the anti-backdrive mechanism.

FIGS. T1 through T12 show an anti-backdrive mechanism 1000 thatincorporates a spring lock. Once again the overall assembly is composedof three main sub-assemblies that move relative to one another: an inputshaft assembly 1002 shown in FIG. T1, an output shaft assembly 1004shown in FIG. T2 and a fixed assembly 1006 shown in FIG. T3. Thecomplete spring-lock assembly incorporating anti-backdrive mechanism1000 is shown in FIG. T4.

The input assembly 1002 includes an input shaft 1008 and a spring 1010.As shown in FIG. T1, the input shaft 1008 is shaped like a cylindricalrod that is tapered for roughly one inch at about a thirty degree angleat one end 1012. The tip of end 1012 is cut off along a planeperpendicular to the longitudinal axis through the shaft to form a bluntpoint 1014. The thirty degree cut forming the taper at end 1012 is notcut uniformly along a plane over the whole region of the shaft butrather the sides 1016 of the shaft follow the thirty degree angled cutwhile a concave recessed area 1018 is carved out moving in from sides1016 towards the interior of the shaft. The recessed area 1018 getsdeeper moving inward reaching all the way down to the center of theshaft near the beginning of the taper, as shown in the cross-sectionalview of FIG. T5. From there the bottom of the recessed area 1018continues longitudinally toward the end of the shaft for about half thelength of the tapered end along a nearly horizontal line 1020. Line 1020then expands to form a flat surface 1022 which is slanted following thetaper but at an angle slightly less than thirty degrees and continues tothe end of the shaft. Surfaces 1024 join the flat surface 1022 to sides1016 along the tapered end 1012 and are sloped downward moving outwardfrom the interior of the shaft. Surfaces 1024 also extend back alongcurved contours to either side of line 1020 joining line 1020 to thesides 1016 of the tapered cut. Spring 1010, shown isolated in FIGS. T6through T8, is shaped like a coil of roughly four turns and fits overthe end of the tapered end 1012 of the input shaft. The ends 1026 of thespring are bent radially inward for about one-quarter inch and arepositioned across from each other within a 120 degree section of thecoil such that they mirror each other when the spring is viewed from thefront. Spring ends 1026 lie against surfaces 1022 on either side of theflat surface 1022, as shown in FIG. T9.

The output assembly 1004 consists only of an output shaft which isshaped like a cylindrical rod with an end 1028 which is tapered andshaped in the same way as the input shaft 1008, as shown in FIG. T2.

FIG. T3 shows fixed assembly 1006 which consists of a mounting block1030, a fixed cylinder 1032, two spacer mounts 1034 and a set screw1036. The mounting block is rigidly attached to the internal structureof the saw. As shown in the exploded view of FIG. T10, mounting block1030 is shaped like a block that has a square face and is about one-halfinch thick with a large hole 1038 in the center through which fits thefixed cylinder 1032. Fixed cylinder 1032 is shaped like a plain hollowcylinder almost two inches long. Set screw 1036 threads into a smallhole 1040 along the top of the mounting block and contacts the outersurface of the fixed cylinder 1032 so that it does not move relative tothe mounting block. A cylindrical spacer mount 1034, which is shapedlike a hollow cylinder at a constant outer diameter for one inch and athin section of larger outer diameter 1042 at one end, is inserted intoeach end of the fixed cylinder 1032 with the larger diameter sections1042 situated outside the fixed cylinder as they are of too large adiameter to fit within the fixed cylinder.

The anti-backdrive mechanism is assembled with the input shaft 1008 andoutput shaft 1004 aligned concentrically with the tapered end 1028 ofthe output shaft overlapping the tapered end 1012 of the input shaft andoriented such that the recessed areas 1018 of each tapered end face eachother, as shown in FIG. T11. The tapered end of the output shaft isinserted into spring 1010, about three-quarters of the way along thetapered end from the end of the shaft so that the sides 1016 of thetapered end nearly contact the ends 1026 of spring 1010 which arewrapped around the tapered end of the input shaft. A spacer mount 1034is placed over the input and output shafts with the larger diametersections 1042 of the spacer mounts facing outward and with spring 1010situated between the inward facing ends of the spacer mounts, as shownin FIG. T12. As mentioned earlier, the spacer mounts fit within thefixed cylinder 1032 which is sized so that spring 1010 makes contactwith the inner surface of the fixed cylinder in the default state of theanti-backdrive mechanism.

When the output shaft starts to rotate, one side 1016 of the tapered end1028 of the output shaft contacts the nearest end 1026 of spring 1010which is wrapped around the input shaft. As the output shaft pushes onthe end of the spring it tends to unwind the spring increasing thediameter of the coil of the spring causing the spring to become wedgedagainst the inner surface of the fixed cylinder 1032 which prevents theoutput shaft from rotating. Attempting to rotate the output shaft in theother direction causes the other side 1016 of the tapered end 1028 ofthe output shaft to contact the nearest end 1026 of spring 1010 againtending to unwind spring 1010 wedging the spring against the innersurface of the fixed cylinder and preventing the output shaft fromfurther rotating.

As the input shaft rotates, the tapered end 1012 of the input shaft 1008pushes against one end 1026 of spring 1010 which tends to wind thespring thus decreasing the diameter of the coil of the spring releasingthe spring from the inner surface of the fixed cylinder so that it isfree to rotate within the fixed cylinder. Thus, as the input shaftrotates, so does spring 1010 and output shaft 1004. Rotating the inputshaft in the other direction causes the tapered end 1012 of the inputshaft to push against the other end 1026 of the spring which again tendsto wind the spring thus decreasing the diameter of the coil of thespring releasing the spring from the fixed cylinder so that the inputshaft, spring and output shaft may rotate.

FIGS. TB1 through TB33 shows an anti-backdrive mechanism 1100 alsoincorporating a spring lock. Once again the overall assembly is composedof three main sub-assemblies that move relative to one another: an inputshaft assembly 1102 shown in FIG. TB1, an output shaft assembly 1104shown in FIG. TB2 and a fixed assembly 1106 shown in FIG. TB3. Thecomplete assembly incorporating the spring-lock anti-backdrive mechanism1100 is shown in FIG. TB4.

FIG. TB5 shows an exploded view of the input assembly 1102 of theanti-backdrive mechanism which includes an input shaft 1108 attached toan input engager 1110 by a set screw 1112. As shown in FIGS. TB6 throughTB8 the input shaft 1108 is shaped like a cylindrical rod which has asection 1114 of slightly smaller diameter at one end that is about oneand a half inches long and which is cut straight across longitudinallyat a depth of about one-fifth the diameter of section 1114 leaving aflat surface 1116 along the length of section 1114. The other end of theinput shaft is cut longitudinally for about one inch along the shaft ata depth of about one-fourth of the diameter of the shaft to create aflat surface 1118 for mounting the elevation handwheel. A groove 1120 ispositioned along the cylindrical portion of the shaft about two inchesin from the smaller diameter section 1114 and in which is installed aneclip 1122.

The input engager 1110, shown isolated in FIGS. TB9 through TB15, has anoverall shape like a short thick-walled hollow cylinder 1124 aboutthree-quarter inch long positioned inside and merged with a longerhollow cylinder 1126 of about two inches long which has a large portionof the surrounding wall removed. Cylindrical section 1126 of the inputengager is first cut longitudinally along each side of the input engagerbeginning at the end with the inner cylindrical section 1124 withlongitudinal cut 1127 ending at the end of section 1126 and longitudinalcut 1129 stretching a little further. The longitudinal cuts 1127 and1129 are made at an angle to the radius of the cylinder moving inwardfrom the outer surface of the input engager towards the innercylindrical section 1124 forming flat angled surfaces 1128 and 1130 thatrun parallel to the axis of the input engager but are at about aforty-five degree angle to the radius of the input engager. The angledsurfaces 1128 and 1130 slope in such a way that a greater arc length iscovered in traveling from one angled surface to the other along theoutside surface of the input engager than would be covered in sweepingthrough the same arc section at the diameter of the inner cylindricalsection of the input engager, as can be seen in FIG. TB11. Angledsurfaces 1128 and 1130 are cut symmetrically so as to mirror each otherwhen the input engager is viewed from the front, as shown in FIG. TB11.Angled surface 1130, which appears on the right in FIG. TB11, runs alongthe length of the inner cylindrical section 1124 and the other angledsurface 1128, which appears on the left in FIG. TB11, runs a littlefarther so that it covers about two-thirds the length of the inputengager as can be seen on the right in FIG. TB9 which shows a view ofthe bottom of the input engager with the input engager rotated so thatthe bottom view faces the open area in the cylinder wall. At the end ofeach of the longitudinal cuts 1127 and 1129 the input engager is cut atabout a forty-five degree angle to a plane through the axis of the inputengager and these forty-five degree cuts 1131 and 1133 form surfaces1132 and 1134 that are at an angle to the radius moving inward just likeangled surfaces 1128 and 1130 and which travel along the sides of thecylinder enclosing more of the space within the engager so that by thetime the cuts exit the engager about three-fourths of the circumferenceof the engager remains, as shown in FIG. TB14. Surface 1132 continues tothe end of the input engager, as can be seen in FIG. TB9. Surface 1134,which appears to the right when the input engager is viewed from therear with the open portion along the side of the input cylinder facingdownward as shown in FIG. TB11, ends shortly before the end of the inputengager, as can be seen in FIG. TB9, and is joined to a short flatsurface 1136 formed by another longitudinal cut 1135 that runs to theend of the input engager parallel to the axis of the input engager ascan be seen in FIGS. TB9 and TB14. Surface 1136 is cut at an angle tothe radius moving inward similarly to surfaces 1128, 1130, 1132 and1134. A distance of a little less than half an inch can be seen betweenthe two forty-five degree cuts 1131 and 1133 when the input engager isviewed from the side, as shown in FIG. TB14. The end of input shaft 1108is inserted into hole 1137 which passes through the center ofcylindrical section 1124 entering hole 1137 from the end that is withinthe input engager so that the end of the input shaft is flush with theend of the input engager when fully inserted and the shaft runs all theway through the input engager. A set screw 1112 threads into a smallhole 1138 located on the outer surface of the engager which passesthrough the inner cylindrical section 1124 and empties into hole 1137 tomake contact with flat surface 1116 on the input shaft. An eclip 1122fits within groove 1120 to position the input shaft within theanti-backdrive mechanism.

FIG. TB16 shows an exploded view of the output assembly 1104 of theanti-backdrive mechanism which includes an output shaft 1140 attached toan output engager 1142 by a set screw 1144. As shown in FIGS. TB17 andTB18 the output shaft 1140 is shaped like a cylindrical rod with asection 1146 of slightly smaller diameter at one end which runs forabout one and one-half inches and which is cut longitudinally along theshaft at a depth of about one-fifth the diameter of section 1146 leavinga flat surface 1148 along the length of the smaller diameter section1146.

The output engager 1142, shown isolated in FIGS. TB19 through TB23, hasan overall shape like a cylinder that is mostly hollow except that it isenclosed on one end with a thick wall 1150 that has a hole 1152 throughthe center for the output shaft 1140 and there is a section 1154 ofgreater wall thickness along the inner cylinder wall which extends fromwall 1150 to the end of the output engager and covers about one-fourththe inner circumference of the output engager. Section 1154 is cut insuch a way as to create two ramps 1156 and 1158, shown best in thecross-sectional view of FIG. TB20. Cuts 1159 and 1161 are madelongitudinally along section 1154 starting from the inner surface ofwall 1150 and running parallel to the axis, creating a flat surface1160, which appears on the right when the output engager is viewed fromthe front and oriented such that section 1154 is at the bottom of theengager and flat surface 1162, which appears on the left when the outputengager is viewed from the front and oriented such that section 1154 isat the bottom as shown in FIG. TB21. Surface 1160 continues for aboutone and a half inches and surface 1162 continues for about one inch onthe other side, as shown in FIGS. TB19 and TB20. Surfaces 1160 and 1162are at an angle to the radius of the outer cylinder and slope in thenegative and positive directions respectively when the output engager isviewed from the front with section 1154 at the bottom, as shown inFigure TB21. At the end of cuts 1159 and 1161, the cylinder is cut at anangle and these cuts 1163 and 1165 form ramp 1156 at the end of flatsurface 1160 and ramp 1158 at the end of flat surface 1162. Each ramp isabout one inch long with ramp 1156 starting about one-half inch beforeramp 1158 begins. Ramp 1156 extends to the end of the output engagerwhile ramp 1158 ends about one-half inch before the end of the cylinderand another longitudinal cut creates a flat surface 1164 which runs fromthe end of ramp 1158 to the end of the output engager. As shown in FIG.TB22, a small hole 1166 is located on the outer surface of the outputengager near the enclosed end and empties into hole 1152 that runsthrough the center of wall 1150. Output shaft 1140 is inserted into hole1152 and a set screw 1144 threads into hole 1166 and contacts the flatsurface 1148 of the output shaft to secure the output shaft to theoutput engager.

FIG. TB24 shows an exploded view of fixed assembly 1106 which consistsprimarily of a mounting block 1168, a fixed cylinder 1170 and a spring1172. The mounting block 1168 is shaped like a three-dimensional ‘E’oriented sideways such that the openings between the three legs of the‘E’ open out to the side and with the middle extension located closer tothe leg of the ‘E’ at the rear than at the front. There is a hole ineach metal slab forming a leg of the ‘E’ which is centered verticallyand located closer to the open end of the ‘E’. The hole 1174 through thefront metal slab, or leg of the ‘E, is larger than the holes 1176through the other two metal slabs, or legs of the ‘E’. One end of fixedcylinder 1170 is inserted into hole 1174 in the mounting block. Fixedcylinder 1170, shown isolated in Figures TB26 through TB28, is shapedlike a hollow cylinder with two narrow sections 1178 of slightly largerdiameter spaced nearly equally along the outside of the fixed cylinderand about a little over one-half inch apart. There is a groove 1180 onthe outside surface at one end of the fixed cylinder for an eclip 1182and at the other end of the cylinder a cut is made longitudinally aboutas deep as about one-eighth the diameter of the cylinder leaving a flatsurface 1184 that ends just before the nearest narrow section 1178. Theend of fixed cylinder 1170 which has flat surface 1184 is inserted intoa hole 1174 at the end of the mounting block 1168 and a set screw 1186threads into a small 1187 on the side of the mounting block whichempties into hole 1174 so that the set screw 1186 makes contact with theflat surface 1184 on the fixed cylinder to secure the fixed cylinder tothe mounting block. Spring 1172, which is shaped like a coil as shown inFIGS. TB29 through TB31, fits over the end of the fixed cylinder betweenE-clip 1182 and the nearest narrow section 1178, as shown in FIG. TB3.The two ends 1188 of spring 1172 exit outward from the coil at an angleof a little over ninety degrees with the winding leading to each end.The two spring ends are spaced so that there is about one-quarter thecircumference of the coil between them. The ends exit the coilsymmetrically so that they mirror each other when the spring is viewedfrom the front about a line drawn through the coil in the middle of thetwo ends of the spring. Two small stress diffusers 1189 are placed onthe spring, one on each end 1188 of the spring. The stress diffusers1189 have a generally rectangular shape with a small hole 1190 throughthe center of the large faces for the end of the spring to fit throughwithout falling out. Stress diffuser 1189 are sized to fit within thegaps that are left between the angled cuts on the input and outputengagers when the input and output engagers are assembled, as shown inFIG. TB32.

The anti-backdrive mechanism is assembled with the input shaft runningthrough the middle of the fixed cylinder 1170 and through hole 1174 inthe mounting block. Eclip 1122, which is placed around the input shaftin groove 1120, is positioned within a recessed area 1191 on the outsideof the mounting block around hole 1174. A thin, rectangular shaped metalplate 1192 with a large hole 1193 in the center of it and two smallholes 1194, one above and one below the hole in the center, is placedover the end of the mounting block and secured by two screws 1195 one ofwhich passes through each hole 1194 and into corresponding holes 1196 inthe mounting block to cover recessed area 1191 and eclip 1122, as shownin FIG. TB25. The input engager is oriented with respect to the fixedcylinder such that the ends 1188 of spring 1172 run parallel to theangled surfaces 1132 and 1134 of the cuts 1131 and 1133 along the sidesof the input engager. The spring end 1188 nearest the end of the fixedcylinder 1170 resides alongside the 45 degree angled cut 1131 whichappears on the left of the input engager when the input engager isviewed from the rear and oriented such that the portion along the sideof the input engager that is removed faces downward, as shown in FIG.TB11. Angled cut 1131 continues to the end of the input engager toaccommodate the movement of spring end 1188 and the stress diffuser 1189placed on the end of the spring. The other spring end, which is next toone of the narrow sections 1178 of slightly larger diameter, is near the45 degree angled cut 1133 which appears on the right of the inputengager when the input engager is viewed from the front and orientedsuch that the portion along the side of input engager that is removedfaces downward. Angled cut 1133 begins and ends earlier than angled cut1131 to accommodate the movement of the end of the spring and the stressdiffuser 1189 placed on the end of the spring which are located furtheralong the fixed cylinder. The output shaft 1140 runs through holes 1176in the other two legs of the ‘E’ shaped mounting block, as shown in FIG.TB4. The input and output shafts are aligned concentrically and theinput engager is inserted into the output engager with the outputengager oriented such that longitudinal cut 1159 in the output engagerruns alongside the longitudinal cut 1127 in the input engager with a gap1197 of about a little less than half an inch between them, as shown inFIG. TB32, and the longitudinal cut 1161 in the output engager runsalongside the longitudinal cut 1129 in the input engager with asimilarly sized gap 1198 between them. Likewise, the 45 degree angledcut 1163 of the output engager runs alongside the 45 degree angled cut1131 of the input engager with gap 1197 running in between them, and 45degree angled cut 1165 of the output engager runs alongside the 45degree angled cut 1133 of the input engager with gap 1198 running inbetween them. The ends 1192 of spring 1172 fit through the gaps 1197 and1198 on either side of the spring and the stress diffuser 1189 on eachspring end fit within gaps 1197 and 1198 and are oriented such that thelong sides of the rectangular shaped stress diffuser 1189 lie parallelto the angled cuts 1131 and 1133, as shown in FIGS. TB32 and TB33.

When the output shaft starts to rotate clockwise, when viewed from thefront, surface 1158 contacts the side of stress diffuser 1189 on the endof the spring 1172 and pushes upon the end of the spring in thedirection that tends to wind the spring more tightly around the fixedcylinder. The tightly wound spring prevents the output shaft fromturning so that neither the output shaft nor the input shaft can rotate.When the output shaft starts to rotate counter-clockwise, surface 1156contacts the side of stress diffuser 1189 on the other end of the spring1172 on the other side of the input engager and pushes upon the end ofthe spring in the direction which again tends to wind the spring. Thus,neither the output shaft nor the input shaft rotates when the outputshaft is rotated.

When the input shaft starts to rotate clockwise, when viewed from thefront, surface 1132 of angled cut 1131 contacts the side of stressdiffuser 1189 on the end of the spring 1172 and pushes upon the end ofthe spring in the direction that tends to unwind the spring. As thediameter spring expands, the spring loosens about the fixed cylinder andis free to rotate as the input shaft rotate and stress diffuser 1189pushes against the surface 1156 on the output engager so that the outputengager rotates as the input engager rotates. When the input shaftrotates counter-clockwise, surface 1134 of angled cut 1133 contacts theside of stress diffuser 1189 on the end of the spring 1172 on the otherside of the input engager and pushes upon the end of the spring in thedirection which again tends to unwind the spring and stress diffuser1189 pushes against the surface 1158 on the output engager so that theoutput engager rotates as the input engager rotates. Thus, the outputshaft rotates when the input shaft is rotated.

FIGS. TA1 through TA4 show another anti-backdrive mechanism 1200 alsoincorporating a spring lock. Once again the overall assembly is composedof three main sub-assemblies that move relative to one another: an inputshaft assembly 1202 shown in FIG. TA1, an output shaft assembly 1204shown in FIG. TA2 and a fixed assembly 1206 shown in FIG. TA3. Thecomplete assembly incorporating the spring-lock anti-backdrive mechanism1200 is shown in FIG. TA4.

The input assembly 1202, shown in FIG. TA1, consists of one piece shapedlike a cylindrical rod 1208, which serves as the input shaft, joined toa rather narrow rectangular extension 1210 with a width that is the sizeof the diameter of the cylindrical rod and which is oriented such thatthe long side extends out perpendicularly from near one end of the rod.A rectangular block 1212 of about the same width of the rectangularextension is joined to the end of the narrow rectangular extension 1210and is oriented so that the long side of the rectangular block runsparallel to the rod. The surface at the end of the rectangular extensionabuts the surface of one of the long, narrow sides of the rectangularblock and the surface of the long face of the rectangular extensionclosest the end of the cylindrical rod is flush with the surface of oneof the short sides of the rectangular block so that the rectangularblock is supported at one end, the end of the rectangular block nearestthe end of the cylindrical rod, so that the rectangular block is held ata distance from and parallel to the cylindrical rod with open space inbetween the rectangular block and the cylindrical rod.

The output assembly, shown in FIG. TA2, consists of one piece shapedlike a long section 1214 of cylindrical rod, which serves as the outputshaft, followed by a short section 1216 of increasing diameter which isin turn followed by a section 1218 of larger diameter which is abouthalf as long as the section of smaller diameter. At the end of thelarger diameter section 1218 there is a triangular extension 1220 shapedlike an isosceles triangle and oriented so that the end of the sectionof larger diameter extends into and forms one corner of the triangle andis flush with the outside surface of the triangle opposite the side ofthe triangle that the rod enters. The triangular extension isperpendicular to the cylindrical rod and the two corners opposite thecorner through which the section 1218 of larger diameter passes eachhave a generally rectangular extension 1222 that runs parallel to therod in the direction opposite to the cylindrical rod. One edge 1224along each of the rectangular extensions is rounded on the corner thatfaces the other extension and is flush with the end of the triangularextension.

FIG. TA3 shows the fixed assembly which consists of a rather thin,rectangular plate 1226, a hollow fixed cylinder 1228 and a spring 1230.The fixed cylinder 1228 passes through a large hole 1232 in the centerof the rectangular plate and the spring 1230 fits around the fixedcylinder. The spring 1230 is shaped like a coil with two long straightends 1234 extending tangentially out from either side of the coil sothat the two long straight ends run parallel to each other. The tips1236 of the long straight ends are curved ninety degrees outward andpoint away from each other. Four small holes 1238, one located in eachcorner of the rectangular plate, are used for rigidly mounting the fixedassembly to the internal structure of the saw so that the fixed assemblydoes not move when other parts of the anti-backdrive mechanism move.

As shown in FIG. TA4, the anti-backdrive mechanism is assembled with thecylindrical rod 1208 of the input assembly passing through hole 1240which runs through the center of the hollow fixed cylinder 1228 of thefixed assembly from the side of the fixed cylinder that has the springmounted to it and out to the other side of the rectangular plate 1226.The rectangular block 1212 on the input assembly fits in between thelong straight ends 1234 of spring 1230. The output assembly is alignedwith the input assembly such that the cylindrical section 1214 of theoutput assembly is concentric with the cylindrical rod 1208 of the inputassembly and the end of the output assembly with the triangularextension 1220 abuts the end of the input assembly near rectangularblock 1212. The rectangular extensions 1222 on the triangular extension1220 of the output assembly straddle the rectangular block 1212 and thelong straight ends 1234 of spring 1230.

When the output shaft, or cylindrical rod 1214, starts to rotateclockwise, as seen from the front, the rectangular extension 1222 of thetriangular extension 1220 pushes against one of the long straight ends1234 of spring 1230 in a direction that tends to wind the spring moretightly around the fixed cylinder. This prevents the output shaft, andthus the input shaft, from rotating. Rotating the output shaft in thecounter-clockwise direction causes the rectangular extension on theother side of the rectangular block 1212 to push against the other longstraight end 1234 of spring 1230 again preventing the output and inputshaft from rotating.

When the input shaft starts to rotate clockwise, as seen from the front,a different situation arises as the rectangular block 1212 pushesagainst one of the long straight ends 1234 of spring 1230 in a directionthat tends to push the long straight end of the spring away from thefixed cylinder 1228 slightly unwinding the spring. With the springloosened around the fixed cylinder, it is free to rotate. The longstraight end 1234 of the spring upon which the rectangular block ispushing contacts the nearest rectangular extension 1222 of thetriangular extension 1220 to transmit the rotating motion of the inputshaft to the output shaft. Rotating the input shaft in thecounter-clockwise direction causes the rectangular block 1212 to contactthe other long straight end 1234 of spring 1230 in a direction whichagain tends to loosen the spring around the fixed cylinder allowing thespring to rotate and the long straight end 1234 of the spring upon whichthe rectangular block is pushing contacts the nearest rectangularextension 1222 of the triangular extension 1220 to transmit the rotatingmotion of the input shaft to the output shaft. Thus, whether the inputshaft turns clockwise or counter-clockwise, both the input shaft and theoutput shaft are able to rotate.

FIGS. CL1 through CL14 show another example of an anti-backdrivemechanism. This anti-backdrive mechanism 900 uses the orientation of twoplates relative to a fixed structure to lock or unlock the mechanism.Once again the overall assembly is composed of three mainsub-assemblies: an input shaft assembly 902 shown in FIG. CL1, an outputshaft assembly 904 shown in FIG. CL2 and a fixed assembly 906 shown inFIG. CL3. The complete assembly incorporating anti-backdrive mechanism900 is shown in FIG. CL4.

The input assembly 902, shown in FIG. CL1 and in the exploded view ofFIG. CL6, consists of a slotted plate 908 fitted on the end of an inputshaft 910 and a collar 912 situated on the input shaft between theslotted plate and the rest of the input shaft and attached to the inputshaft by a set screw 914. Slotted plate 908, shown isolated in FIGS. CL7through CL9, is shaped like a narrow square plate a couple inches wide.There is a hole 916 passing through the center of the plate that iscircular for about 270 degrees but is cut straight along one side withthe straight cut 918 running parallel to one side of the plate. Oneither side of the center hole 916 there are rectangular slots 920running perpendicular to the straight cut in the center hole, one sloton each side of the center hole 916. The slots are almost as long as theplate with a border left between each slot and the edge of the plate.Three sides of each slot are cut straight through the plate so that theyleave surfaces along the edges of the slots that fall on planes whichare parallel to the edge of the plate, but the long side 922 of eachslot closest to the edge of the plate are cut through the plate along aplane that is at an angle of about sixty degrees, as shown best in thecross-sectional view of FIG. CL7. The slotted plate 908 fits over theend of the input shaft which has a section 924 of smaller diametercompared to the rest of the cylindrical shaft which is shaped to matchthe hole at the center of the slotted plate, that is, it is shaped likea cylindrical of smaller diameter cut longitudinally to form a flatsurface 926 along the section. The circular collar 912 also fits overthe end of the input shaft and is situated between the slotted plate andthe long section of the input shaft which has a larger diameter. Setscrew 914 threads into a hole 928 in the collar and makes contact withthe flat surface 926 along section 924 of the input shaft to attach thecollar to the input shaft. At the end of the input shaft opposite theend to which the plate is mounted, there is a section of slightlysmaller diameter which is also cut longitudinally to form a flat surface928 which is used to mount a handwheel.

The output assembly, shown in FIG. CL2 and in the exploded view of FIG.CIAO, consists of an output shaft 930, a spacer collar 932 and a spring934. The output shaft 930 is shaped like a cylindrical rod with a hole936 passing through the shaft near one end. Collar 932 is generallyrectangular but with the short sides rounded so that they bow outward.Coaxially aligned holes 938 run through the long sides of the collar anda large hole 940 passes through the center of the collar. The outputshaft fits through hole 940 in the collar which is positioned near oneend of the output shaft. Spring 934 fits through hole 938 on one side ofcollar 932, then through hole 936 in the output shaft and finallythrough hole 938 on the other side of collar 932. Spring 934 is longenough to extend out from collar 932 by about one-quarter to one-halfinch on each side of the collar.

The fixed assembly, shown in FIG. CL3 and in the exploded view of FIG.CL11, consists of a fixed brake plate 942 and two rotating plates 944.Fixed brake 942 is shaped like a narrow plate with a basically squareface and a large circular hole 946 which passes through the plate fromthe front face to the rear. A rectangular block 948 of about one-fourththe width of the plate is vertically oriented and runs along one edge ofthe plate to rigidly mount the plate to the internal structure of thesaw. Holes 950 located near the top and bottom of the rectangular block948 and passing front to back are used for screws that attach therectangular block to the brake plate 942, and two more holes 952 whichpass through the rectangular block from the side to side are used forscrews to rigidly mount the brake plate to the internal structure of thesaw. Rotating plates 944, shown isolated in FIGS. CL12 through CL14, aregenerally rectangular plates with notches 954 cut out of the top andbottom sides near one end. Notches 954 are cut such that each looks likea square cut all the way through the rotating plate when looking down atthe face of the rotating plate, as shown in FIG. CL14. When lookingalong the outside edge of the rotating plate along which the notch iscut out, however, notch 954 looks more like an ‘X’ in that the sides ofthe notch are cut at angles. As can be best seen in FIG. CL13 whichshows a side view of the rotating plate 944 facing notch 954, the angledcut along the side of notch 954 that appears to the left in FIG. CL13consists of a short segment 956 of negative slope which joins a longersegment 958 of positive slope. The short segment 956 of a negative slopestarts from the top face of the plate at a point between the edge of thelong side that appears to the left on the rotating plate in FIG. CL13and the middle of the long side of the rotating plate but closer to themiddle, and stops before reaching the midline running longitudinallythrough the long side of the rotating plate. The longer segment 958starts where the short segment stops and continues towards the bottomface of the rotating plate along a positive slope. The angled cut alongthe side of notch 954 that appears to the right in FIG. CL13 is alsomade up of two segments, a longer segment 958 with a positive slope anda shorter segment 956 with negative slope. The longer segment 958 startsfrom the top face of the rotating plate at a point between the edge ofthe long side that appears to the right on the rotating plate in FIG.CL13 and the middle of the long side of the rotating plate but closer tothe middle, and stops just beyond the midline running longitudinallythrough the long side of the rotating plate at which point it joins theshorter segment 956 of negative slope that continues toward and stops atthe bottom face of the rotating plate. The points at which the longerand shorter segments 958 and 956 of each angled cut meet forms peaks 960and 962 which are rounded and slightly set off from each other as theupper and lower sloped segments on each side are of a slightly differentlength with the peak 960 that appears along the left side of the notchin FIG. CL13 positioned a little above the longitudinal midline of thelong side of the rotating plate and peak 962 that appears along theright side of the notch in FIG. CL13 positioned a little below thelongitudinal midline of the side.

As shown in FIGS. CL4 and CL5, the anti-backdrive mechanism is assembledwith the input and output shaft coaxially aligned with the slotted plateof the input shaft positioned at the rear of the fixed brake plate 942and the input shaft extending through the large circular cutout 946 inthe fixed brake plate out towards the front. Collar 912 on the inputshaft is situated between the rotating plates 944 at the end of therotating plates which have notches 954. Collar 930 on the output shaftis situated between the rotating plates 944 on the other side of theslotted plate 908 at the end of the rotating plates without notches 954.Spring 934 presses against the inner faces of the rotating plates 944and the sides 922 of slots 920 in the slotted plate that are cut at anangle allow sprint 934 to push the rotating plates outward so that theyare at an angle to the fixed brake plate 942.

When the output shaft 930 starts to rotate in either the clockwise orcounter-clockwise direction, as seen from the front, spring 934 whichpushes against the inner faces of the rotating plates 944, keeps theplates pushed outward away from each other and at an angle to the fixedbrake plate 942 so that peaks 960 and 962 on each rotating plate arewedged against the fixed brake plate preventing the rotating plates, andthus the input shaft, from rotating.

When the input shaft starts to rotate clockwise, as seen from the front,a different situation arises as the slotted plate 908 on the input shaftpushes against the rotating plates 944 compressing spring 934 on thecollar of the output shaft and pulling the rotating plates inward as theslotted plate rotates and the distance between the contact points atwhich the slotted plate applies the turning force on each rotating plateis reduced. As the rotating plates are drawn together they become moreperpendicular to the fixed brake plate and there is more space betweeneach side of the fixed brake plate and peaks 960 and 962 so that therotating plates are free to rotate. Rotating the input shaft in thecounter-clockwise direction causes the same effect only the contactpoints are at the opposite corners of each rotating plate. The rotatingplates contact spring 934 in the collar on the output shaft and transmitthe rotating motion to collar 932 on the output shaft which rotates theoutput shaft. Thus, whether the input shaft turns clockwise orcounter-clockwise, both the input shaft and the output shaft are able torotate.

FIGS. CW1 through CW11 show another example of an anti-backdrivemechanism. This anti-backdrive mechanism 1300 uses the orientation oftwo plates relative to a fixed structure to lock or unlock themechanism. Once again the overall assembly is composed of three mainsub-assemblies: an input shaft assembly 1302 shown in FIG. CW1, anoutput shaft assembly 1304 shown in FIG. CW2 and a fixed assembly 1306shown in FIG. CW3. The complete assembly incorporating anti-backdrivemechanism 1300 is shown in FIG. CW4.

The input assembly 1302, shown in FIG. CW1 and in the exploded view ofFIG. CW6, consists of a slotted plate 1308 fitted on the end of an inputshaft 1310 shaped like a cylindrical rod. Slotted plate 1308, shownisolated in FIGS. CW9 through CW11, is shaped like a circular plate withtwo flat sides 1311 on opposite sides of the plate. There is a hole 1312passing through the center of the plate that extends through a smallcylindrical extension 1314 on the front face of the slotted plate. Oneither side of the center hole 1312 there are rectangular slots 1316with rounded corners running perpendicular to the flat sides 1311, oneslot on each side of the center hole 1312. The slots are almost as longas the plate. The slotted plate 1308 fits over the end of the inputshaft which has a section 1318 of smaller diameter compared to the restof the cylindrical shaft which is shaped to match the hole at the centerof the slotted plate. A set screw 1320 threads into a hole 1322 in thecylindrical extension 1314 and then through hole 1324 in the smallerdiameter section 1318 of the input shaft to attach the slotted plate1308 to the input shaft 1310. At the end of the input shaft opposite theend to which the plate is mounted, there is a section which is cutlongitudinally to form a flat surface 1326 which is used to mount ahandwheel.

The output assembly, shown in FIG. CW2 and in the exploded view of FIG.CW7, consists of an output shaft 1328, a collar 1330 and a spring 1332.The output shaft 1328 is shaped like a cylindrical rod with twogenerally rectangular projections 1334 sticking out longitudinally fromone end which are parallel to each other with a gap 1336 between them.The rectangular projections 1334 are formed as of from a cylinder ofsmaller diameter than the diameter of the output shaft and positionedconcentrically with the output shaft. There are two holes 1338 and 1340in each rectangular projection 1334 and the holes in one rectangularprojection are aligned with the holes in the other rectangularprojection, for example, hole 1340 in one rectangular projection isdirectly across from hole 1340 in the other rectangular projection. Theholes are aligned along the midline running parallel to the rectangularprojections and holes 1340 are slightly larger than holes 1338. Collar1330 is shaped like a hollow cylinder which abuts the face of a narrowblock that is generally rectangular but with the short sides 1341rounded so that they bow outward. Coaxially aligned holes 1342 runthrough the long sides of the collar and a large hole 1344 passesthrough the center of the rectangular section of the collar. The outputshaft fits through the middle of the hollow cylindrical section of thecollar. A pin 1348 passes through a small hole 1350 in the cylindricalsection of the collar that runs along the radius of the cylindricalsection perpendicular to the shaft then through holes 1338 in therectangular projections of the output shaft then through another smallhole 1350 on the other side of the cylindrical section of the collar tosecure the collar 1330 to the output shaft. Spring 1332 fits throughhole 1342 on one side of collar 1330, then through holes 1340 in therectangular projections of the output shaft and finally through hole1342 on the other side of collar 1330. Spring 1332 is long enough toextend out from collar 1330 by around one-quarter inch on each side ofthe collar.

The fixed assembly, shown in FIG. CW3 and in the exploded view of FIG.CW8, consists of a fixed brake plate 1352 and two rotating plates 1354.Fixed brake 1352 is shaped like a narrow plate with a basically squareface and a large circular hole 1356 which passes through the plate fromthe front face to the rear. A rectangular block 1358 of about one-fourththe width of the plate is vertically oriented and runs along one edge ofthe plate to rigidly mount the plate to the internal structure of thesaw. Holes 1360 located near the top and bottom of the rectangular block1358 and passing front to back are used for screws that attach therectangular block to the brake plate 1352, and two more holes 1362 whichpass through the rectangular block from the side to side are used forscrews to rigidly mount the brake plate to the internal structure of thesaw. Rotating plates 1354 are shaped like narrow rectangular slabs withholes 1364 and 1366 drilled near the center of surfaces 1368 along thelong, thin side edges of the plate so that the holes run parallel to theplate and are coaxially aligned with the holes 1364 and 1366 drilledinto surfaces 1368 on the opposite sides of the plates. Holes 1364 arelocated closer to one face of the plate and holes 1366 are locatedcloser to the other face of the plate. A metal dowel pin 1370 isinserted into each of the four holes 1364 and 1366 in each rotatingplate and extend outward from the edges of the plate about one-quarterinch. The rotating plates are oriented so that they are parallel to eachother and fit through the large circular cutout 1356 in the fixed brakeplate with each pair of pins 1370 on the same plate side edge straddlingthe brake plate. Holes 1364, which are closer to the faces of therotating plates pointing inward, are positioned near the back side ofthe brake plate and holes 1366, which are closer to the faces of therotating plates pointing outward are positioned near the front side ofthe brake plate, as can be seen in FIG. CW5.

As shown in FIGS. CW4 and CW5, the anti-backdrive mechanism is assembledwith the input and output shafts coaxially aligned and collar 1330 ofthe output shaft positioned on the front side of the fixed brake plate1352 and in between the rotating plates 1354 so that the ends of spring1332 contact the inward pointing faces of the rotating plates pushingthe rotating plates outward so that they are at an angle to the fixedbrake plate and the metal dowel pins 1370 are wedged against the brakeplate. The slotted plate 1308 on the end of the input shaft fits overthe ends of the rotating plates with each plate passing though one ofthe rectangular slots 1316 in the slotted plate.

When the output shaft 1328 starts to rotate spring 1332 keeps therotating plates pushed outward so that the dowel pins 1370 remain wedgedagainst the fixed brake plate preventing the rotating plates fromrotating. When the input shaft starts to rotate a different situationarises as the slotted plate pulls the ends of the rotating platestogether enough to release the dowel pins 1370 from the fixed brakeplate allowing the rotating plates to rotate freely which then transmitthe rotating motion to the output shaft through collar 1330 on theoutput shaft. Thus, both the input shaft and the output shaft are ableto rotate when the input shaft is rotated.

FIGS. E1 through E16 show various embodiments of elevation mechanismsthat may be incorporated into a saw to raise or lower the blade. Some ofthese embodiments can raise or lower the blade is just a few turns ofthe handwheel.

FIG. E1 shows an elevation mechanism 1400 that uses a rack and pinion.Pinion gear 1402 is mounted at the end of the output shaft 1404 androtates as the handwheel 1406 rotates. Block 1408 in FIG. E2 representsan anti-backdrive mechanism connecting the input shaft 1410 to theoutput shaft 1404. The teeth of the pinion gear mate with the teethalong a rack 1412 that is attached to a structure 1414 that is free toslide up and down a vertically oriented elevation shaft 1416 rigidlymounted to the saw 1418 and is used to support the blade so that aspinion gear 1402 rotates rack 1412 is moved up or down raising andlowering structure 1414 thus changing the elevation of the blade.

FIGS. E3 and E4 show an elevation mechanism 1440 that uses a set ofmiter gears 1442 and 1444 and a single threaded rod 1446. Because themiter gears prevent the input shaft from being back-driven there is noneed for an anti-backdrive mechanism and a single shaft 1448 serves asboth the input and output shaft. Miter gear 1442 is attachedconcentrically at the end of the shaft 1448 and mates with miter gear1444 that is vertically mounted to the lower of two support structures1450 that are rigidly attached to the internal structure of the saw 1418and which surrounds the top and bottom ends of the vertically orientedthreaded rod 1446 to keep it in position. A short threaded cylinder 1452is threaded onto the threaded rod and is attached to the blade supportstructure 1412 that is free to slide up and down a vertically orientedelevation shaft 1416 rigidly mounted to the saw 1418 and is used tosupport the blade. As the threaded rod rotates, threaded cylinder 1452moves up or down along the threaded rod thus changing the elevation ofthe blade.

FIGS. E5 and E6 show an elevation mechanism 1460 that uses a groovedbelt 1462 that wraps around a threaded shaft 1464. Belt 1462 haslongitudinal grooves molded along the width of one side that mate withthe grooves on the threaded shaft to which the handwheel 1406 ismounted. The ends of the belt are attached to the top and bottom ends ofthe structure 1412 that is free to slide up and down a verticallyoriented elevation shaft 1416 rigidly mounted to the saw 1418 and isused to support the blade. As the handwheel rotates, the belt shifts onthe threaded shaft as they wrap further in one direction along the shaftand unwraps in the other direction so that a different segment along thebelt remains wrapped around the threaded shaft. As more of the beltcloser to the end that is attached near the top of the structure thatsupports the blade is drawn closer to and wraps around the threadedshaft, the structure that supports the blade moves downward and theblade is lowered. As more of the belt closer to the end that is attachednear the bottom of the structure that supports the blade is drawn closerto and wraps around the threaded shaft, the structure that supports theblade moves upward and the blade is raised.

FIGS. E7 and E8 show an elevation mechanism 1470 that uses a cable 1472on a threaded shaft 1474. The cable is attached at the top to a block1476 rigidly attached to the blade support structure 1412, runsvertically downward, wraps around the threaded shaft 1474 about fivetimes within and following the grooves on the threaded shaft, runsvertically downward and loops at the bottom around another block 1476rigidly attached to the blade support structure 1412 and runs back upwrapping around the threaded shaft several times again within andfollowing a parallel track of grooves and continues up and attaches tothe blade support structure next to where the other end of the cable isattached. Block 1408 in FIG. E8 represents an anti-backdrive mechanismconnecting the input shaft 1478 to which the handwheel is attached andthe threaded shaft 1474. FIG. E9 shows the cable 1472 isolated.

FIGS. E10 through E12 show an elevation mechanism 1480 that uses a cable1482 wrapped around a large, fairly narrow, circular spool 1484 that isrotated by a gear 1486 and worm gear 1488. Worm gear 1488 is mounted atthe end of the shaft 1490 to which the handwheel 1406 is attached andmates with gear 1486 which is mounted on a shaft 1492 that is orientedabove and at a right angle to shaft 1490. Spool 1484 is mounted on theother end of shaft 1492. Cable 1482 is attached at the top end to ablock 1494 that is rigidly attached to the blade support structure 1412that is free to slide up and down a vertically oriented elevation shaft1416 rigidly mounted to the saw 1418 and is used to support the blade.The cable continues vertically downward and wraps under and around spool1484 and then continues downward where it is attached at the bottom endto another block 1494 that is rigidly attached to structure 1412. As thehandwheel 1406 rotates, shaft 1490 rotates and attached worm gear 1488rotates which rotates gear 1486 and attached spool 1484. As spool 1484rotates, cable 1482 winds and unwinds around the spool so that adifferent portion of the cable wraps around the spool drawing one end ofthe cable closer to the spool and allowing the other end to move fartheraway from the spool thus raising or lowering structure 1412 and theblade depending on the direction the handwheel is rotated. The spool issized so that it only takes about one full rotation of the handwheel tomove structure 1412 and thus the blade through the full range ofelevation from a fully lowered blade to a fully raised blade.

FIGS. E13 and E14 show an elevation mechanism 1500 that uses two cables1502 and 1504 that partially wrap along the outside of a large, fairlynarrow, swinging arc sector 1506 that is rotated by a gear 1508 and wormgear 1510. Worm gear 1510 is mounted at the end of the shaft 1512 towhich the handwheel 1406 is attached and mates with gear 1514 which ismounted on a shaft 1516 that is oriented above and at a right angle toshaft 1512. Swinging arc section 1506, shaped like a large, thick arcsection of a little less than one-fourth a circle, is mounted on theother end of shaft 1512. Cable 1502 is attached at the top end to ablock 1518 that is rigidly attached to the upper part of the bladesupport structure 1412 that is free to slide up and down a verticallyoriented elevation shaft 1416 rigidly mounted to the saw 1418 and isused to support the blade. Cable 1502 continues vertically downward andruns along the outside of swinging arc section 1506 and is attached tothe swinging arc section on the curved outside surface near the bottomof the curved outside surface. Cable 1504 is attached at the bottom endto another block 1518 that is rigidly attached to the lower part ofstructure 1412 and continues upward and runs along the outside ofswinging arc section 1506 and is attached to the swinging arc section onthe curved outside surface near the top of the curved outside surface.As the handwheel 1406 rotates, shaft 1512 rotates and attached worm gear1510 rotates which rotates gear 1514 and attached swinging arc section1506. As Swinging arc section 1506 rotates, one of the cables 1502 or1504, depending on the direction that the handwheel is rotated, windsabout the swinging arc sector 1506 while the other cable unwinds drawingthe end of the cable attached to a block 1518 closer to the swinging arcsector and allowing the end of the other cable attached to the otherblock 1518 to move farther away from the swinging arc sector thusraising or lowering structure 1412 and the blade depending on thedirection the handwheel is rotated. The swinging arc sector can be sizedso that it only takes about one full rotation of the handwheel to movestructure 1412 and thus the blade through the full range of elevationfrom a fully lowered blade to a fully raised blade.

FIGS. B15 and E16 shows an elevation mechanism 1540 that uses a cable1542 and a worm gear 1544. Worm gear 1544 is mounted at the end of anoutput shaft 1546 and rotates as the handwheel 1406 rotates. Block 1548in FIG. E16 represents an anti-backdrive mechanism connecting the inputshaft 1550 to the output shaft 1546. Cable 1542 is attached at one endto a block 1552 attached to the upper part of the blade supportstructure 1412 that is free to slide up and down a vertically orientedelevation shaft 1416 rigidly mounted to the saw 1418 and is used tosupport the blade. Gable 1542 continues vertically downward and wrapsaround worm gear 1544 several times following the grooves in the wormgear and then continues downward and attaches to another block 1552attached to the lower part of structure 1412. As handwheel 1406 rotates,input shaft 1550 and output shaft 1546 rotate and attached worm gear1544 rotates. As the worm gear 1544 rotates, cable 1542 winds andunwinds around the worm gear so that a different portion of the cablewraps around the worm gear drawing one end of the cable closer to theworm gear and allowing the other end to move farther away from the wormgear thus raising or lowering structure 1412 and the blade depending onthe direction the handwheel is rotated. The worm gear is sized and thenumber of times the cable is around the worm gear is chosen so that itonly takes about one full rotation of the handwheel to move structure1412 and thus the blade through the full range of elevation from a fullylowered blade to a fully raised blade.

FIG. E17 shows an elevation mechanism using levers. A lever 1550 extendsout from the saw and a user pivots the lever to raise and lower theblade. Linkage inside the saw connects to lever 1550 so that movement ofthe lever raises and lowers the blade.

FIGS. E18 through E25 show an elevation limit stop 1600 that preventsthe handwheel 1602 from being rotated past the point where the bladereaches the fully elevated or fully lowered position according to thedesign of the saw. If the handwheel is forced beyond the proper limits,parts within the saw could be bent or otherwise damaged. As shown inFIGS. E22 through E25 limit stop 1600 is shaped like a thick, wide ringwith an arc section 1602 of larger diameter sweeping through an angle ofabout 100 degrees or so which extends out from the ring. A secondsmaller arc section 1604 shaped similarly to section 1602 but sweepingthrough a slightly smaller angle of 90 degrees is layered on top ofsection 1602 nearly doubling the thickness of the limit stop where thetwo arc sections overlap. Arc section 1604 is centered within arcsection 1602 and is set back a small distance from the inner surface ofthe ring. Limit stop 1600 fits over the input shaft 1606, is free torotate on the shaft, and is oriented such that the smaller arc section1604 faces the handwheel. An adjustable screw 1607, shown in FIG. E21,extends from the internal structure of the saw and acts as an abutmentagainst which stop 1600 abuts. Limit stop 1600 is also positioned on theinput shaft near a pin 1608 which extends out radially from the inputshaft. Pin 1608 moves with the input shaft as the input shaft rotates.As pin 1608 rotates, it contacts one edge of arc section 1604 and causesthe limit stop to rotate with the shaft until the limit stop abutsagainst screw 1607 and stops the shaft from rotating. FIG. E19 shows theinput shaft rotated clockwise until pin 1608 is up against one edge ofarc section 1604 of the limit stop, and FIG. E20 shows the inputs shaftrotated counter-clockwise until pin 1608 is up against the opposite edgeof arc section 1604 of the limit stop.

FIG. TF1 shows a tool or jig 1700 used to assemble an embodiment of ananti-backdrive mechanism similar to anti-backdrive mechanism 26described in FIGS. 3-38, but with a modified flange plate and a modifiedvertical plate. The modified flange plate is shown in FIGS. TF2 and TF3at 1702, and the modified vertical plate is shown in FIG. TF4 at 1704.

Tool 1700 is typically machined from aluminum, or made from some otherappropriate material, and can be attached to a table or workbench. Tool1700 has walls 1706 and 1708 shaped to receive the various components ofthe anti-backdrive mechanism. Tool 1700 also has slots or channels 1710and 1712 which provide clearance for the tabs 1714 and 1716,respectively, which extend from the back of flange arms of spring 102.(Tabs 1714 and 1716 are used to transmit torque to an output shaft inone embodiment of an elevation mechanism.) Tool 1700 also includes fourposts or projections 1718, 1720, 1722 and 1724 that extend throughcorresponding slots in the flange plate (the slots are seen in FIGS. TF2and TF3, but are not labeled). The posts are used to position flangeplate 1702 in the tool. The posts are arcuate and posts 1718 and 1720have shorter arc lengths than posts 1722 and 1724. The slots in theflange plate are also arcuate and have different arc lengths so thatflange plate 1702 can be placed in tool 1700 in only one orientation.

To assemble an anti-backdrive mechanism, a person first places a flangeplate in tool 1700, as explained. The person next places vertical plate1704 over the flange plate. Tool 1700 is constructed so the verticalplate must be oriented correctly to fit in the tool. The tool includesears 1726 and 1728 that interfere with mounting flanges 1730 on thevertical plate if the person assembling the mechanism attempts to placethe vertical plate in the tool incorrectly. The person also places afoam or felt ring in the tool, such as foam filter 172 discussedpreviously, and places a spring in the tool, such as torsion spring 102discussed previously. Flange plate 1702 includes a center post overwhich the spring is placed. Additionally, the person places two lockingsprings 138 on posts 136 on the flange plate, one locking spring on eachpair of posts, and places locking cylinders 140 on the ends of thelocking springs. Locking springs 138 are then compressed so the two armsof one locking spring fit between posts 1718 and 1720 and the two armsof the other locking spring fit between posts 1722 and 1724. In thismanner the posts hold the springs compressed while the anti-backdrivemechanism is assembled. FIG. TF5 shows tool 1700 with the flange plate,locking springs and locking cylinders installed.

A release plate 40 is then installed in the tool, as shown in FIG. TF6.A ramp plate 44 is placed over the assembly, a foam or felt ring 1732 isplaced around the release plate, and the assembly is held together withtwo screws, as shown in FIG. TF7.

FIGS. Z1 through Z11 show another embodiment of an elevation mechanismwith anti-backdrive. As seen in FIG. Z1, a trunnion 2000 supports anelevation carriage 2002, and elevation carriage 2002 is configured tomove up and down on rod 2004 (rod 2004 is attached to trunnion 2000). Ina table saw, elevation carriage 2002 supports a circular blade and amotor to drive the blade. The elevation carriage, and therefore theblade, moves up and down by a user turning handwheel 2006.

Handwheel 2006 is connecting to an input shaft 2008 which is connectedto an anti-backdrive mechanism 2010. An output shaft 2012 extends fromanti-backdrive mechanism 2010 and terminates with a spool or reel 2012shaped like a worm gear. A cable 2016 is connected at a first end 2018to a first location on elevation carriage 2002, and at a second end 2020to a second location on the elevation carriage. Between its two ends,the cable is wound around spool 2012. Specifically, first end 2018 ofcable 2016 includes a fitting 2017, shown in FIG. Z2, attached to thecable by crimping or some other method. Fitting 2017 fits into a socketat the first location on elevation carriage 2002 to secure the first endof the cable to the elevation carriage. Second end 2020 of cable 2016includes a threaded-shaft fitting 2021 crimped or otherwise joined tothe cable, as shown in FIG. Z2. Elevation carriage 2002 includes aflange/socket structure configured to support a coil spring 2023 at thesecond location. The threaded-shaft fitting extends through an openingin the flange/socket structure, through spring 2023, through a washer atthe top of the spring, and then a nut 2024 is threaded onto the threadedshaft to secure the second end of the cable to the elevation carriageand to compress spring 2023. FIG. Z3 shows a simplified and enlargedview of fitting 2021 and spring 2023. Spring 2023 functions to take upslack in the cable if the cable stretches over time during use. Spring2023 also functions somewhat to absorb sudden impacts that mightotherwise strain or break the cable.

Cable 2016 includes a locator or stop 2025 attached to the cable betweenits two ends. Stop 2025 fits into a recess in spool 2014, as shown inFIG. Z4, and thereby locates the cable relative to the spool andprevents the cable from slipping on or around the spool.

With this configuration, turning handwheel 2006 causes shafts 2008 and2012 and spool 2014 to rotate. That causes cable 2016 to wind and unwindon spool 2014, and that, in turn, causes the elevation carriage to moveup and down.

As shown in FIG. Z1, a coil spring 2030 is positioned around shaft 2012.One end of the coil spring is attached to trunnion 2000 by passingthrough a bracket 2026 which is mounted to the trunnion, as shown inFIG. Z5, and the other end of the spring is attached to shaft 2012. Theweight of elevation carriage 2002, the blade, and the motor can besubstantial, and spring 2030 provides a force to assist in raisingelevation carriage 2002 and to balance the force required on thehandwheel to raise and lower the blade. The tension on the spring andthe spring force can be selected to provide the desired assistance andbalance. Without the spring, the handwheel could be too hard to turn toraise the blade, and/or could be too easy to turn to lower the blade.

The elevation mechanism shown in FIG. Z1 also includes an overload shockabsorber 2050. In a table saw with active injury mitigation technologyas disclosed in International Patent Publication WO 01/26064 A2,published Apr. 12, 2001, and hereby incorporated by reference, the sawmay stop and/or retract the blade if a person comes into contact with ordangerous proximity to the spinning blade, and that reaction mightcreate an impulse or shock on the elevation mechanism. Alternatively, asaw may be dropped or otherwise impacted, and the drop or impact maycreate an impulse or shock on the elevation mechanism. Overload shockabsorber 2050 works to accommodate or absorb any such impact or shock tominimize the likelihood of damage to the elevation mechanism.

Overload shock absorber 2050 is shown in more detail in Figures Z6through Z9. It includes two shock plates 2052 and 2054. FIG. Z7 shows ashock plate isolated from other structure. Each shock plate includes asomewhat hour-glass shaped opening 2056 at its center, and each shockplate is slid onto the end of shaft 2012 opposite spool 2014, as shownin the exploded view of FIG. Z8. The end of shaft 2012 is shaped to havea generally rectangular cross-section that fits within openings 2056 inthe shock plates. However, the generally hour-glass shape of openings2056 provide clearance around the end of shaft 2012 so the shock platescan rotate somewhat around the shaft before the sides of the openingsabut the sides of the shaft. Shock plates 2052 and 2054 are identical,but one is turned before it is slid onto the shaft so that the two shockplates are oriented in what may be thought of as opposite each other. Acap 2053 fits over the end of shaft 2012 to hold the shock plates on theshaft, and the cap is secured on the shaft with a screw 2055.

Shock plates 2052 and 2054 each include arms 2060, and coil springs 2062and 2064 are positioned over the arms of both shock plates, as shown inFIG. Z6. The springs, therefore, help hold the two shock platestogether. The coil springs are compressed when installed on the arms ofthe shock plates so the springs tend to push the shock plates apartuntil a side of opening 2056 in each shock plate contacts a side of thegenerally rectangular-shaped end of shaft 2012.

As seen in FIG. Z9, an input coupler 2070 is placed over the shockplates on the side away from spool 2014. The input coupler is operablyconnected to anti-backdrive mechanism 2010, which is operably connectedto shaft 2008, so the input coupler rotates when a user turns handwheel2006. Input coupler 2070 includes two shoulders or projections 2072 and2074 that fit between shock plates 2052 and 2054. Shoulders 2072 and2074 transmit torque from shaft 2008 to shaft 2012 through the shockplates. Springs 2062 and 2064 allow the transmission of torque up to amagnitude required to further compress the springs. However, if there issome event or impact causing a sudden torque of sufficient magnitude tofurther compress the springs, then springs 2062 and 2064 will compressand absorb at least some of the force of the impact.

As can be seen, overload shock absorber 2050 allows for the transmissionof torque up to a predetermined threshold before absorbing additionaltorque. By so doing, the elevation mechanism maintains a solid, rigidfeel at handwheel 2006 and the elevation mechanism does not feel spongy.This feature may be thought of as positive zeroing because it positivelytransmits torque at the zero or balanced state, absorbs shock whenoverloaded, and then returns to the zero or balanced state.

FIG. Z10 shows an exploded view of handwheel 2006. The handwheelincludes a handle body 2100 with recesses around its periphery, such asrecess 2102. A soft, tactile material 2104, such as rubber or softplastic, is applied to the recesses around the periphery of the handlebody to provide a tactile gripping surface. The end of input shaft 2008is hex-shaped, and a splined connector 2106 is configured to fit overthe end of input shaft 2008. The backside of handle body 2100 includes asocket 2108 to fit over the splined connector, as shown in FIG. Z11, andthe handle body is attached to input shaft 2008 with a washer, lockwasher, screw and cap, as shown in Figure. Z10. A knob 2110 is attachedto the handle body by a bolt 2112 that screws into a threaded insert2114, and a cap 2116 fits over the end of the knob, as shown in FIG.Z10. Knob 2110 may rotate around bolt 2112 so that a user can grasp theknob and turn the handwheel without the knob twisting in the user'shand. The knob is positioned away from the center axis of rotation ofthe handle body to create a moment arm to make turning the handwheeleasier.

INDUSTRIAL APPLICABILITY

The blade elevation mechanisms and anti-backdrive mechanisms disclosedherein are applicable to woodworking power tool equipment, andparticularly to table saws. The anti-backdrive mechanisms discussedabove may be referred to as anti-backdrive means for preventing theblade from unwanted retraction, means for preventing back-drive, or someother similar appellation.

It is believed that the disclosure set forth above encompasses multipledistinct inventions with independent utility. While each of theseinventions has been disclosed in its preferred form, the specificembodiments thereof as disclosed and illustrated herein are not to beconsidered in a limiting sense as numerous variations are possible. Thesubject matter of the inventions includes all novel and non-obviouscombinations and sub-combinations of the various elements, features,functions and/or properties disclosed herein. No single feature,function, element or property of the disclosed embodiments is essentialto all of the disclosed inventions. Similarly, the recitation of “a” or“a first” element, or the equivalent thereof, should be understood toinclude incorporation of one or more such elements, neither requiringnor excluding two or more such elements.

The elevation mechanisms and related components disclosed herein may bedescribed generally as set forth in the following numbered paragraphs.These paragraphs are intended as illustrative, and are not intended tolimit the disclosure or claims in any way. Changes and modifications maybe made to the following descriptions without departing from the scopeof the disclosure.

1. A table saw comprising:

a table defining a work surface;

a substantially planar, circular blade configured to extend at leastpartially above the work surface;

a motor to spin the blade; and

an elevation system configured to change the elevation of the bladerelative to the work surface;

where the elevation system includes a rotatable handwheel adapted to beturned by a user to raise and lower the blade; and

where the elevation system is configured so that the blade can movebetween a fully lowered position and a fully elevated position with 15turns or less of the handwheel.

2. A table saw comprising:

a table defining a work surface;

a substantially planar, circular blade configured to extend at leastpartially above the work surface;

a motor to spin the blade; and

an elevation system configured to change the elevation of the bladerelative to the work surface;

where the elevation system includes a rotatable handwheel adapted to beturned by a user to raise and lower the blade; and

where the elevation system is configured so that the blade can movebetween a fully lowered position and a fully elevated position with 5turns or less of the handwheel.

3. A table saw comprising:

a table defining a work surface;

a substantially planar, circular blade configured to extend at leastpartially above the work surface;

a motor to spin the blade; and

an elevation system configured to change the elevation of the bladerelative to the work surface;

where the elevation system includes a rotatable handwheel adapted to beturned by a user to raise and lower the blade; and

where the elevation system is configured so that the blade can movebetween a fully lowered position and a fully elevated position with 3turns or less of the handwheel.

4. A table saw comprising:

a table defining a work surface;

a substantially planar, circular blade configured to extend at leastpartially above the work surface;

a motor to spin the blade; and

an elevation system configured to change the elevation of the bladerelative to the work surface;

where the elevation system includes a rotatable handwheel adapted to beturned by a user to raise and lower the blade; and

where the elevation system is configured so that the blade can movebetween a fully lowered position and a fully elevated position with 1turn or less of the handwheel.

5. A table saw comprising:

a table defining a work surface;

a substantially planar, circular blade configured to extend at leastpartially above the work surface;

a motor to spin the blade; and

an elevation system configured to change the elevation of the bladerelative to the work surface;

where the elevation system includes a rotatable handwheel adapted to beturned by a user to raise and lower the blade; and

where the elevation system is configured to move the blade at least 3inches with 15 turns or less of the handwheel.

6. A table saw comprising:

a table defining a work surface;

a substantially planar, circular blade configured to extend at leastpartially above the work surface;

a motor to spin the blade; and

an elevation system configured to change the elevation of the bladerelative to the work surface;

where the elevation system includes a rotatable handwheel adapted to beturned by a user to raise and lower the blade; and

where the elevation system is configured to move the blade at least 3inches with 5 turns or less of the handwheel.

7. A table saw comprising:

a table defining a work surface;

a substantially planar, circular blade configured to extend at leastpartially above the work surface;

a motor to spin the blade; and

an elevation system configured to change the elevation of the bladerelative to the work surface;

where the elevation system includes a rotatable handwheel adapted to beturned by a user to raise and lower the blade; and

where the elevation system is configured to move the blade at least 3inches with 3 turns or less of the handwheel.

8. A table saw comprising:

a table defining a work surface;

a substantially planar, circular blade configured to extend at leastpartially above the work surface;

a motor to spin the blade; and

an elevation system configured to change the elevation of the bladerelative to the work surface;

where the elevation system includes a rotatable handwheel adapted to beturned by a user to raise and lower the blade; and

where the elevation system is configured to move the blade at least 3inches with 1 turn or less of the handwheel.

9. The table saw of any of paragraphs 1-8, where the elevation system isfurther configured to prevent gravity from moving the blade from a firstposition at a first elevation to a second position at a second elevationwhen a user releases the handwheel, where the second elevation is atleast 5% less than the first elevation.

10. The table saw of any of paragraphs 1-8 where the elevation system isfurther configured to prevent gravity from causing the blade to dropmore than an insignificant amount when a user releases the handwheel.

11. The table saw of any of paragraphs 1-8 where the elevation system isfurther configured so that gravity does not cause the blade to drop morethan a quarter of an inch when a user releases the handwheel.

12. The table saw of any of paragraphs 1-11 where the elevation systemincludes an anti-backdrive mechanism.

13. A table saw comprising:

a table defining a work surface;

a substantially planar, circular blade configured to extend at leastpartially above the work surface;

a motor to spin the blade;

a rotatable handwheel adapted to be turned by a user to raise and lowerthe blade; and

elevation means for moving the blade at least 3 inches with 15 turns orless of the handwheel and for preventing backdrive of the blade.

14. An anti-backdrive mechanism for table saws comprising:

a handwheel;

an input shaft assembly operatively associated with the handwheel;

an output shaft assembly; and

back-drive structure operatively connecting the input shaft assembly andthe output shaft assembly so that a torque on the input shaft assemblyturns the output shaft assembly, but a torque on the output shaftassembly does not turn the input shaft assembly.

15. The anti-backdrive mechanism of paragraph 14, where the input shaftassembly, the output shaft assembly, and the back-drive structure areconfigured to occupy a neutral position where friction preventsback-drive, and further configured to occupy a non-neutral positionwhere the input shaft assembly moves the output shaft assembly when thehandwheel turns.

16. The anti-backdrive mechanism of paragraph 14, further comprising afriction component and a friction surface, where the friction componentengages the friction surface sufficiently to prevent back-drive when theinput shaft assembly, the output shaft assembly, and the back-drivestructure occupy the neutral position, and where the friction componentdoes not engage the friction surface sufficiently to prevent back-drivewhen the input shaft assembly, the output shaft assembly, and theback-drive structure occupy a non-neutral position.

17. A table saw comprising:

a table defining a work surface;

a substantially planar, circular blade configured to extend at leastpartially above the work surface;

a motor to spin the blade;

a rotatable handwheel adapted to be turned by a user to raise and lowerthe blade;

an input assembly associated with the handwheel;

an output assembly; and

a fixed assembly operatively connecting the input assembly and theoutput assembly so that turning the handwheel transmits a torque to theoutput assembly to raise or lower the blade, but the weight of the bladeand supporting structure does not backdrive the blade.

18. An elevation mechanism for table saws comprising:

a hand wheel;

a shaft structure associated with the hand wheel;

a moveable elevation carriage to support a blade; and

a cable interconnecting the shaft structure and the elevation carriage.

19. The elevation mechanism of paragraph 18 where the cable winds andunwinds around at least a portion of the shaft structure to raise andlower the blade.

20. The elevation mechanism of paragraph 18 or 19, further comprising ananti-backdrive mechanism.

21. The elevation mechanism of any one of paragraphs 18-20, furthercomprising a spring associated with the cable to bias against slack inthe cable.

22. The elevation mechanism of any one of paragraphs 18-22, furthercomprising an overload shock absorber configured to allow for thetransmission of torque up to a predetermined threshold before absorbingadditional torque.

23. An elevation mechanism for table saws having blades, the elevationmechanism comprising:

a rotatable hand wheel; and

means for raising a blade at least 3 inches with 5 turns or less of thehand wheel.

24. A table saw comprising:

a table defining a work surface;

a substantially planar, circular blade configured to extend at leastpartially above the work surface;

a motor to spin the blade;

an elevation system configured to change the elevation of the bladerelative to the work surface, where the elevation system includes arotatable handwheel adapted to be turned by a user to raise and lowerthe blade, and where the elevation system is configured to move theblade at least 3 inches with 5 turns or less of the handwheel; and

an overload shock absorber.

25. A table saw comprising:

a table defining a work surface;

a substantially planar, circular blade configured to extend at leastpartially above the work surface;

a motor to spin the blade; and

an elevation system configured to change the elevation of the bladerelative to the work surface, where the elevation system includes arotatable handwheel adapted to be turned by a user to raise and lowerthe blade, where the elevation system is configured to move the blade atleast 3 inches with 5 turns or less of the handwheel, and where theelevation system includes an overload shock absorber configured to allowfor the transmission of torque up to a predetermined threshold andthereafter to absorb at least some additional torque.

26. A table saw comprising:

a table defining a work surface;

a substantially planar, circular blade configured to extend at leastpartially above the work surface;

a motor to spin the blade;

an elevation system configured to change the elevation of the bladerelative to the work surface, where the elevation system includes arotatable handwheel adapted to be turned by a user to raise and lowerthe blade, and where the elevation system is configured to move theblade at least 3 inches with 5 turns or less of the handwheel; and

an elevation limit stop configured to prevents the handwheel from beingrotated past the point where the blade reaches a fully elevated or afully lowered position.

27. A tool to assemble an anti-backdrive mechanism.

It is believed that the following claims particularly point out certaincombinations and sub-combinations that are directed to disclosedinventions and are novel and non-obvious. Inventions embodied in othercombinations and sub-combinations of features, functions, elementsand/or properties may be claimed through amendment of the present claimsor presentation of new claims in this or a related application. Suchamended or new claims, whether they are directed to a differentinvention or directed to the same invention, whether different, broader,narrower or equal in scope to the original claims, are also regarded asincluded within the subject matter of the inventions of the presentdisclosure.

1. A table saw comprising: a table defining a work surface; asubstantially planar, circular blade configured to extend at leastpartially above the work surface; a motor to spin the blade; anelevation system configured to change the elevation of the bladerelative to the work surface, where the elevation system includes ahandwheel adapted to be turned by a user to raise the blade from a fullylowered position to a fully elevated position with 5 turns or less ofthe handwheel; and an anti-backdrive mechanism configured to preventgravity from causing the blade to drop more than a quarter of an inchwhen a user releases the handwheel.
 2. The table saw of claim 1 wherethe elevation system is configured so that the blade can be raised froma fully lowered position to a fully elevated position with 3 turns orless of the handwheel.
 3. The table saw of claim 1 where the elevationsystem is configured so that the blade can be raised from a fullylowered position to a fully elevated position with 1 turn or less of thehandwheel.
 4. The table saw of claim 1 where the anti-backdrivemechanism comprises: an input shaft assembly operatively associated withthe handwheel; an output shaft assembly; and back-drive structureoperatively connecting the input shaft assembly and the output shaftassembly so that a torque on the input shaft assembly turns the outputshaft assembly, but a torque on the output shaft assembly does not turnthe input shaft assembly.
 5. The table saw of claim 4 where the inputshaft assembly, the output shaft assembly, and the back-drive structureare configured to occupy a neutral position where friction preventsback-drive, and further configured to occupy a non-neutral positionwhere the input shaft assembly moves the output shaft assembly when thehandwheel turns.
 6. The table saw of claim 4, where the anti-backdrivemechanism further comprises a friction component and a friction surface,where the friction component engages the friction surface sufficientlyto prevent back-drive when the input shaft assembly, the output shaftassembly, and the back-drive structure occupy a neutral position, andwhere the friction component does not engage the friction surfacesufficiently to prevent back-drive when the input shaft assembly, theoutput shaft assembly, and the back-drive structure occupy a non-neutralposition.
 7. The table saw of claim 1 where the anti-backdrive mechanismcomprises: an input assembly associated with the handwheel; an outputassembly; and a fixed assembly operatively connecting the input assemblyand the output assembly so that turning the handwheel transmits a forceto the output assembly to raise the blade, but the weight of the bladeand motor does not backdrive the blade.
 8. The table saw of claim 1where the handwheel is configured to rotate around an axis, where thehandwheel includes a handle body configured to rotate around the axis,where the handle body includes a perimeter configured to be grasped by auser, where the handwheel includes a rubber material around at least apart of the perimeter, and where the handwheel includes a knob attachedto the handle body at a position offset from the axis.
 9. A table sawcomprising: a table defining a work surface; a substantially planar,circular blade configured to extend at least partially above the worksurface; a motor to spin the blade; and an elevation system configuredto change the elevation of the blade relative to the work surface, wherethe elevation system includes a handwheel adapted to be turned by a userto change the elevation of the blade by at least 3 inches with 5 turnsor less of the handwheel; and an anti-backdrive mechanism configured toprevent gravity from causing the blade to drop more than a quarter of aninch when a user releases the handwheel.
 10. The table saw of claim 9where the elevation system is configured to change the elevation of theblade at least 3 inches with 3 turns or less of the handwheel.
 11. Thetable saw of claim 9 where the elevation system is configured to changethe elevation of the blade at least 3 inches with 1 turn or less of thehandwheel.
 12. The table saw of claim 9 where the anti-backdrivemechanism comprises: an input shaft assembly operatively associated withthe handwheel; an output shaft assembly; and back-drive structureoperatively connecting the input shaft assembly and the output shaftassembly so that a torque on the input shaft assembly turns the outputshaft assembly, but a torque on the output shaft assembly does not turnthe input shaft assembly.
 13. The table saw of claim 12 where the inputshaft assembly, the output shaft assembly, and the back-drive structureare configured to occupy a neutral position where friction preventsback-drive, and further configured to occupy a non-neutral positionwhere the input shaft assembly moves the output shaft assembly when thehandwheel turns.
 14. The table saw of claim 12, where the anti-backdrivemechanism further comprises a friction component and a friction surface,where the friction component engages the friction surface sufficientlyto prevent back-drive when the input shaft assembly, the output shaftassembly, and the back-drive structure occupy a neutral position, andwhere the friction component does not engage the friction surfacesufficiently to prevent back-drive when the input shaft assembly, theoutput shaft assembly, and the back-drive structure occupy a non-neutralposition.
 15. The table saw of claim 9 where the anti-backdrivemechanism comprises: an input assembly associated with the handwheel; anoutput assembly; and a fixed assembly operatively connecting the inputassembly and the output assembly so that turning the handwheel transmitsa force to the output assembly to raise the blade, but the weight of theblade and motor does not backdrive the blade.
 16. The table saw of claim9 further comprising an overload shock absorber.
 17. The table saw ofclaim 9 where turning the handwheel creates torque, and furthercomprising an overload shock absorber configured to allow for thetransmission of torque by turning the handwheel up to a predeterminedthreshold and thereafter to absorb at least some additional torque. 18.A table saw comprising: a table defining a work surface; a substantiallyplanar, circular blade configured to extend at least partially above thework surface; a motor to spin the blade; a rotatable handwheel adaptedto be turned by a user to raise and lower the blade; and means forraising the blade at least 3 inches from a fully lowered position with 5turns or less of the handwheel and for preventing gravity from causingthe blade to drop more than a quarter of an inch when a user releasesthe handwheel.